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WO2005080755A1 - Pompes de type gerotor perfectionnees - Google Patents

Pompes de type gerotor perfectionnees Download PDF

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Publication number
WO2005080755A1
WO2005080755A1 PCT/US2004/002778 US2004002778W WO2005080755A1 WO 2005080755 A1 WO2005080755 A1 WO 2005080755A1 US 2004002778 W US2004002778 W US 2004002778W WO 2005080755 A1 WO2005080755 A1 WO 2005080755A1
Authority
WO
WIPO (PCT)
Prior art keywords
gerotor
floating ring
mesh
outer rotor
juxtaposed
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US2004/002778
Other languages
English (en)
Inventor
Edward H. Phillips
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Performance Pumps LLC
Original Assignee
Performance Pumps LLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Performance Pumps LLC filed Critical Performance Pumps LLC
Priority to PCT/US2004/002778 priority Critical patent/WO2005080755A1/fr
Publication of WO2005080755A1 publication Critical patent/WO2005080755A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/04—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for reversible machines or pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine

Definitions

  • the present invention relates generally to gerotor pumps, and more particularly to improved gerotor pumps wherein an outer rotor of gerotor sets utilized therein is enabled for finding its own eccentricity offset axis whereat it is supported mechanically via forcibly meshing with the inner rotor at the gerotor set in-mesh position and otherwise in a nominally hydrostatically balanced manner.
  • Gerotor pumps are most conveniently designed around commercially available gerotor gear sets (hereinafter simply "gerotor sets") such as those manufactured by Nichols Portland of Portland, ME.
  • Such gerotor sets comprise an inner rotor having N outwardly extending lobes with N approximately circularly shaped grooves therebetween (i.e., with N typically having values of 4, 6, 8 or 10) in mesh with an eccentrically disposed outer rotor comprising N + 1 inwardly extending circularly shaped elements.
  • the inner rotor is mounted upon and directly driven by the drive shaft of a prime mover such as an electric motor.
  • the eccentrically disposed outer rotor is then driven by the inner rotor via meshing of the outwardly and inwardly extending lobes then instantly located nominally nearest an "in-mesh" position.
  • This meshing contact occurs with near zero relative velocity between inner and outer rotors in the region of the in-mesh position while a maximum relative velocity between tips of the outwardly extending lobes of the inner rotor and the inwardly extending lobes of the outer rotor occurs at the opposite or out-of-mesh position along an eccentricity axis.
  • Present art gerotor pumps typically comprise a fixedly positioned eccentric gerotor pocket within which the outer rotor is supported by a hydrodynamic bearing formed in the space between the eccentric gerotor pocket and the outer rotor.
  • the gerotor pocket is simply formed as part of the pump housing and then completed by a cover plate wherein inner surfaces of the gerotor pocket and cover plate serve as first and second sides of a gerotor cavity.
  • the bore of the eccentric gerotor cavity is formed about a preferred eccentricity offset rotation axis located along a preferred eccentricity axis at a distance nominally equal to a gear addendum.
  • Axially oriented symmetrical fluid commutation ports are formed in either or both of the first and second sides of the gerotor cavity to either side of the preferred eccentricity axis and are fluidly coupled to housing ports.
  • fluid is conveyed from the inlet fluid commutation port to inlet side ones of N + 1 pumping chambers formed between the outwardly and inwardly extending lobes and elements as they move out of mesh on the inlet side, and then out the outlet fluid commutation port via outlet side ones of the N + 1 pumping chambers as they move back toward mesh on the outlet side.
  • the pumping chambers are formed between N nominal line seals provided by the mesh of the outwardly and inwardly extending lobes and elements and an additional nominal line seal between one inwardly extending element and a juxtaposed one of the grooves of the inner rotor nearest the "in-mesh" position.
  • a needle bearing could be used to support the outer rotor for a gerotor pump that rotates at too low a speed to generate sufficient hydrodynamic bearing support.
  • prior art gerotor pumps utilize fixedly positioned eccentric gerotor pockets in concert with meshing gerotor sets. As a result of this they are mechanically over constrained whereby it is impractical to utilize closely fitting inner and outer rotors such as are required for generating high output pressure values. And even with the commonly available relatively loose fitting gerotor sets (e.g., with perhaps 0.003 in. dimetral clearance), the actual driving contact position of mesh between inner and outer rotors is indeterminate.
  • gerotor pumps having an additional degree of freedom and thus permitting their outer rotors to find their own optimum centers of rotation under all conditions of loading and shaft deflection were disclosed.
  • the additional degree of freedom also allowed operation at relatively high output pressure values via utilizing precision formed gerotor sets such as those described in connection with Figs. 33 through 43 of the incorporated '812 patent application.
  • gerotor pumps disclosed therein continued to utilize gerotor sets wherein lobe-to-lobe contact was possible at positions other than at line seals nearest the in- mesh position (i.e., including the out-of-mesh position). Furthermore, imprecisely defined hydrodynamic bearing supported forces were still present in those gerotor pumps. It would be desirable to provide gerotor pumps comprising floating rings wherein these remaining concerns have been addressed.
  • the primary object of the present invention is to provide gerotor pumps wherein gerotor sets are forcibly held in mesh at the in- mesh position whereby the outer rotors are mechanically driven by the inner rotors under nominally zero differential velocity meshing conditions and thereby in a substantially friction- and wear-free manner.
  • an inner rotor of a gerotor set having N outwardly extending lobes with N approximately circularly shaped grooves therebetween is directly driven from a drive motor's output shaft (hereinafter "the drive shaft").
  • the inner rotor then drives an outer rotor of the gerotor set having N + 1 inwardly extending circularly shaped elements about a preferred eccentricity offset rotation axis located generally along a preferred eccentricity axis.
  • the further improved gerotor pumps disclosed herein are nominally configured with the outer rotor being located within a floating ring that is in turn located laterally with respect to the preferred eccentricity axis by orthogonal guide means formed in a housing gerotor pump cavity.
  • the outer rotor is again supported for rotation by a hydrodynamic bearing formed in the space between the outer rotor and floating ring.
  • the outer rotor and the floating ring are nominally allowed to float along the preferred eccentricity axis.
  • the position of the outer rotor along the eccentricity axis is generally determined via allowing the mesh of the outer rotor of the gerotor set to determine its own orthogonal location via meshing action between it and the inner rotor. Then forces generated within the hydrodynamic bearing determine the orthogonal location of the floating ring as well.
  • the gerotor sets of the further improved gerotor pumps are additionally forcibly urged into mesh along the eccentricity axis at the in-mesh position. This is accomplished via hydrostatically sourced loading of the floating ring in the orthogonal direction.
  • delivery pressure is applied to a piston bearing upon the outer surface of the floating ring at a location juxtaposed to the in-mesh position.
  • an orthogonally directed force proportional to the greater of input and delivery pressures is applied to the in-mesh end of the outer rotor. The end result is that the outwardly and inwardly extending lobes of the inner and outer rotors are held tightly in mesh at the in-mesh position whereat there is almost no relative motion between them and only passive contact elsewhere.
  • the outer rotors and floating rings are nominally configured in the manner described in the incorporated '812 patent application with reference to gerotor pump 210 depicted in Fig. 18 therein.
  • enhanced porting is obtained via radial face slots formed in either side of the rotor.
  • these radial face slots convey each individual pumping chamber's pressure to juxtaposed edges of the periphery of the outer rotor. This provides a distribution of pressure around the outer rotor that tends to balance the above mentioned transverse outer rotor loading in the lateral direction.
  • face fluid commutation ports formed in either side of the floating ring.
  • the face fluid commutation ports interdict the radial face slots to provide improved commutation.
  • they convey input and delivery fluid from housing ports and either side of the gerotor pump cavity to and from the appropriate ones of the radial face slots.
  • First and second pins are disposed in first and second slots formed in the outer surface of the floating ring along the eccentricity axis. The pins interface with juxtaposed walls of the pump housing such that they act as check valves in keeping delivery fluid from mixing with inlet fluid.
  • gerotor pump 210 the floating ring is somewhat balanced in the lateral direction as well with a residual lateral force being impressed upon the orthogonal guide means.
  • the gerotor sets of the improved gerotor pumps disclosed in the additional preferred embodiments of the present invention are also forcibly urged into mesh along the eccentricity axis at the in-mesh position.
  • this is accomplished via differential orthogonal hydrostatic loading of the floating ring in combination with nominally identical orthogonal hydrostatic loading of the outer rotor.
  • the required orthogonal loading of the floating ring is effected by equidistant opposite lateral offsetting of similar first and second slots (e.g., to those used in the gerotor pump 210), and therefore similar first and second pins, on either side of the eccentricity axis.
  • first and second holes respectively convey delivery and inlet pressure to first and second cavities respectively formed symmetrically about the eccentricity axis on the inner surface of the floating ring.
  • the first and second cavities are configured such that, in combination with the individual fluid pressures conveyed to the periphery of the outer rotor by the radial face slots, the resulting forces applied to the floating ring along the eccentricity axis are nominally hydrostatically balanced.
  • first pair of pins acting as a pair of check valves that provide the space therebetween with fluid having the higher pressure.
  • the space between the second pair of slots is vented to the lower of inlet and delivery pressures whereby the pin instantly interfacing with the higher pressure fluid acts as a check valve.
  • the second pair of pins acting as a pair of check valves that in this case provide the space therebetween with fluid having the lower pressure.
  • the first and second sets of pins again orthogonally apply force proportional to the difference between delivery and inlet pressures to the in-mesh end of the floating ring as well as keep delivery fluid from mixing with the inlet fluid.
  • first and second holes and cavities are formed in the floating ring such that the outer rotor is forcibly positioned against the inner rotor at the in-mesh position.
  • the floating ring is again substantially balanced in the orthogonal direction.
  • forces otherwise imposed upon the hydrodynamic bearing have been significantly reduced.
  • the outwardly and inwardly extending lobes of the inner and outer rotors are held tightly in mesh at the in-mesh position whereat there is almost no relative motion between them and only passive contact elsewhere. All of this is most important in the case of a reversible pump or hydraulic motor utilized in a servo system wherein very smooth operation at low speeds is required.
  • the present invention is directed to providing improved gerotor pumps wherein outer rotors laterally constrained by floating rings are forcibly positioned against the inner rotors at the in-mesh position.
  • gerotor pumps wherein the outer rotors are additionally balanced in the lateral direction, and concomitantly, the floating rings are balanced in the orthogonal direction.
  • the present invention is directed to improved methods for supporting a gerotor set in a gerotor pump, wherein the methods minimally comprise the steps of: applying force to the floating ring along the eccentricity axis toward the gerotor set's in- mesh position and coupling that force to the juxtaposed space between the floating ring and the outer rotor whereby the outer rotor is forcibly positioned against the inner rotor.
  • Figs. 1A and 1 B are sectional views of an improved gerotor pump according to a preferred embodiment of the present invention
  • Fig. 2 is an exploded isometric view of operative elements of the improved gerotor pump according to the preferred embodiment of the present invention
  • Fig. 3 is a plan view depicting a gerotor set, floating ring and piston utilized in the improved gerotor pump shown in Fig. 2
  • Fig. 4 is a flow chart depicting an improved method for supporting a gerotor set comprised in a gerotor pump
  • Fig. 1A and 1 B are sectional views of an improved gerotor pump according to a preferred embodiment of the present invention
  • Fig. 2 is an exploded isometric view of operative elements of the improved gerotor pump according to the preferred embodiment of the present invention
  • Fig. 3 is a plan view depicting a gerotor set, floating ring and piston utilized in the improved gerotor pump shown in Fig. 2
  • Fig. 4 is a flow chart depicting an
  • FIG. 5 is an exploded isometric view of operative elements of another improved gerotor pump according to a first alternate preferred embodiment of the present invention
  • Fig. 6 is a plan view depicting first and second pins utilized as check valves and pockets utilized for applying orthogonally directed hydrostatic pressure to an outer rotor of the improved gerotor pump shown in Fig. 5
  • Fig. 7 is an exploded isometric view of operative elements of another improved gerotor pump according to a second alternate preferred embodiment of the present invention
  • Fig. 8 is a plan view depicting first and second sets of pins utilized as check valves in the improved gerotor pump shown in Fig. 7
  • Fig. 9 is another flow chart depicting an alternate improved method for supporting a gerotor set comprised in a gerotor pump.
  • a gerotor set 12 comprises an inner rotor 14 having N nominally circularly shaped outwardly extending lobes 16 and an eccentrically disposed outer rotor 18 having N + 1 inwardly extending circularly shaped lobes 20.
  • the gerotor set 12 is inserted in a floating ring 22 that is oriented concentrically about a preferred eccentricity offset rotation axis 24 shown in Figs.
  • the actual orthogonal location of the eccentricity offset rotation axis 24 is determined by the mesh of the inner and outer rotors 14 and 18.
  • the actual lateral position of the eccentricity offset rotation axis 24 is determined by the lateral location of the floating ring 22 as positioned by guide flats 28a and 28b formed on the floating ring 22 slidingly engaging guide shoulders 30a and 30b formed as part of a gerotor pocket 32.
  • the gerotor pocket 32 is formed in a portion of a housing 34 extending beyond a shoulder 38 that terminates a bore 40 formed therein.
  • the bore 40 is formed in a concentric manner with reference to the preferred position of the input shaft axis of rotation 26.
  • N + 1 pumping chambers 36 are formed between N nominal line seals 42 provided by the mesh of the outwardly and inwardly extending lobes 16 and 20 and an additional nominal line seal 42 between one inwardly extending lobe 20 and a juxtaposed one of N grooves 44 of the inner rotor 14 nearest the "in-mesh" position of the gerotor set 12.
  • the inner rotor 14 is directly driven by the output shaft 46 of a drive motor 48 (hereinafter “the drive shaft 46") via a feature enabling transmission of torque from one element to another such as implemented herein by Woodruff key 50.
  • the outer rotor 18 is rotationally driven in turn by the inner rotor 14 via mesh of the inwardly extending lobes 20 with the groove 44 nearest the "in-mesh" position of the gerotor set 12 and a proximate one of the outwardly extending lobes 16 with via line seals 42 formed therebetween.
  • the gerotor pocket 32 is contoured to provide operating clearance for the floating ring 22, and specifically so as to provide freedom of motion in the orthogonal direction for the gerotor set 12 as indicated by numerical indicators 52a and 52b.
  • Inner surface 56 of the gerotor pocket 32 is formed at a slightly greater depth from the shoulder 38 than the axial thickness of the gerotor set 12 whereby the gerotor set 12 is provided with axial operating clearance after a cover plate 58 is inserted into the bore 40 against the shoulder 38 and is forcibly retained thereat by a beveled retaining ring 60.
  • the inner surface 56 and an inner surface 62 of the cover plate 58 respectively serve as first and second sides of a gerotor cavity for the gerotor set 12.
  • a bore 64 formed concentrically in the cover plate 58 receives a pilot boss 66 of the drive motor 48 whereby proper alignment of the drive motor 48 is obtained with reference to the preferred position of the input shaft axis of rotation 26.
  • gerotor pump 10 axially oriented inlet and delivery fluid commutation ports 68a and 68b are formed in the inner surface 56 on either side of the preferred eccentricity axis 54 for selectively conveying fluid from inlet port 70a to the pumping chambers 36, and from the pumping chambers 36 to delivery port 70b.
  • the gerotor pump 10 is assumed to in fact be a pump (e.g., as opposed to a hydraulic motor) with its delivery pressure always exceeding the return pressure.
  • gerotor set 12 is depicted as having a clockwise rotation with axially oriented inlet and delivery fluid commutation ports 68a and 68b respectively located on the left and right sides.
  • the axially oriented inlet and delivery fluid commutation ports 68a and 68b can be formed according to dimensions provided by the gerotor set manufacturer. For instance, such dimensions are tabulated for a wide range of gerotor sets in Fig. 4 of a catalog entitled “Gerotor Selection and Pump Design” available from Nichols Portland (hereinafter “the Nichols Portland catalog”).
  • the outer rotor 18 is of course urged laterally toward the guide shoulders 30a by a force derived from the pressure difference between the fluid pressures present at the axially oriented inlet and delivery fluid commutation ports 68a and 68b.
  • gerotor pump 10 that force is impressed upon the floating ring 22 via a hydrodynamic bearing formed in the space 78 between the outer rotor 18 and the floating ring 22. That force is then impressed upon the housing 34 via the guide shoulders 30a by the guide flats 28a and is then imposed upon the drive motor 48 structure via mounting bolts (not shown). This is balanced by an equal and oppositely directed force imposed upon the drive motor 48 structure via the drive shaft 46 and its shaft bearings 72. Additionally however, in the gerotor pump 10 the floating ring 22 is urged orthogonally toward an in-mesh position 92 of the gerotor set 12 via pressure applied to a piston 74.
  • the piston 74 is mounted in a cylinder bore 76 formed in the housing 34 and bears against a flat surface 80 formed on the floating ring 22. Sufficient clearance is provided between the piston 74 and the cylinder bore 76 to avoid mechanical over constraint otherwise resulting from the piston's engagement with the flat surface 80. Necessary sealing for the piston 74 is provided by an O-ring 82.
  • the pressure applied to the piston 74 is the fluid pressure in the delivery 15 port 70b.
  • the delivery pressure is conveyed from the delivery port 70b to the cylinder bore 76 via a cylinder port 84.
  • the various cavities surrounding the floating ring 22 and drive shaft 46 are vented to the lower valued fluid pressure in the inlet port 70a in a known manner via vent slot 86.
  • piston 74 In order for the piston 74 to provide sufficient force to effect full time engagement of the outer rotor 18 with the inner rotor 14 at the in- mesh position 92, its area must exceed that of half the maximum area between instant line seal 42 positions at the out-of-mesh position 88 as indicated by numerical indicator 90 in Fig. 3. As a practical matter this suggests that relatively wide gerotor sets 12 should be utilized in the gerotor pump 10. This is because piston area is a square law function of its diameter while the minimum required area is a linear function of gerotor set width. For instance, a gerotor set 12 having an inner rotor 14 with six outwardly extending lobes 16 should have a minimum width equal to perhaps 1/3 of the outer diameter of the outer rotor 18.
  • this supplemental orthogonal loading of the floating ring 22 results in a supplemental orthogonal loading of the outer rotor 18 along the eccentricity axis 54 via naturally occurring rotational adjustments within the hydrodynamic bearing formed in the space 78.
  • an orthogonally directed force proportional to the greater of the input and delivery pressures is applied to the in-mesh end of the outer rotor 18 at a location juxtaposed to the in-mesh position 92 of the gerotor set 12.
  • the end result is that one of the grooves 44 and an inwardly extending lobe 20 are held tightly in mesh at the in-mesh position 92 whereat there is little relative motion between them.
  • this method minimally comprises the steps of: applying force to floating ring 22 along the eccentricity axis 54 toward a gerotor set's in-mesh position 92; and coupling that force to the space 78 between the floating ring 22 and an outer rotor 18 whereby the outer rotor 18 is forcibly positioned against an inner rotor 14.
  • Figs. 5 and 6 thereshown in exploded isometric and plan views is an improved unidirectional gerotor pump 100 according to a first alternate preferred embodiment of the present invention.
  • a gerotor set 102 is inserted in a floating ring 104 that is again located laterally via first and second sets of orthogonally directed guide flats 28 formed thereon slidingly engaging first and second sets of orthogonally directed guide shoulders 30 formed as part of a gerotor pocket 106 in a housing 108.
  • the floating ring 104 has face fluid commutation ports 110 formed in either side.
  • the face fluid commutation ports 110 interdict radial face slots 114 formed on either side of an outer rotor 112. In order to effect proper commutation, spacing between ends of the face fluid commutation ports 110 is equal to the width of the radial face slots 114.
  • Fluid communication between the face fluid commutation ports 110 and respective inlet and delivery ports 116a and 116b is generally provided by unrestricted fluid flow through the gerotor pocket 106.
  • Multiple inlet ports 116a are utilized to provide reduced inlet fluid pressure loss and thereby reduce the likelihood of cavitation.
  • bosses 118 are formed on both sides of the lateral portions of the floating ring 104 in order to provide it with yaw stability.
  • First and second slots 120a and 120b are respectively formed on the in-mesh and out-of-mesh ends 124 and 126 of the floating ring 104.
  • the first and second slots 120a and 120b are equidistantly positioned from the eccentricity axis 54 with the first slot 120a positioned toward the inlet side of the gerotor pocket 106 and the second slot 120b positioned toward the delivery side of the gerotor pocket 106. Sealing between the delivery and inlet sides of the gerotor pocket 106 is accomplished via pins 128 freely moving within the first and; second slots 120a and 120b whereby they act as check valves in sealing the nominal clearance space between the floating ring 104 and juxtaposed surfaces 130 of gerotor pocket 106.
  • first and second slots 120a and 120b results in an orthogonal force equal in value to the product of projected orthogonal spacing between pins 128, depth of the gerotor pocket 106, and the difference between delivery and inlet pressures.
  • first and second holes 132a and 132b respectively convey delivery and inlet pressure to first and second cavities 134a and 134b respectively formed symmetrically about the eccentricity axis 54 on the inner surface 136 of the floating ring 104.
  • the first and second cavities 134a and 134b ate configured such that, in combination with individual fluid pressures conveyed to the periphery of the outer rotor 112 by the radial face slots 114, the resulting forces applied to the inner surface 136 of floating ring 104 along the eccentricity axis are in nominal hydrostatic balance with the externally applied orthogonal force.
  • the radial face slots 114 convey each individual pumping chamber's pressure to juxtaposed edges of the periphery of the outer rotor 112. This provides a distribution of pressure around the outer rotor 112 that tends to balance transverse outer rotor loading in the lateral direction.
  • bi-directional operation is provided via insertion of first and second pairs of laterally spaced apart pins 152a and 152b respectively disposed in first and second pairs of slots 154a and 154b formed on the in-mesh and out-of-mesh ends 156 and 158 of yet another floating ring 160, respectively.
  • the individual slots 154 of the first and second pairs of slots 154a and 154b are formed equidistant from the eccentricity axis 54.
  • the slots 154 comprised in the first pair of slots 154a are fluidly coupled one-to-another via linking cavities 162 extruded into the faces of the floating ring 160.
  • first pair of pins 152b acting as a check valve that provides the space bounded by the linking cavities 162 with fluid having the higher pressure.
  • space 164 between the second pair of slots 154b is vented to fluid having the lower pressure in a known manner via check valves 166, a first venting port 168 and a venting slot 170.
  • the cavities surrounding the drive shaft 46 are also vented to fluid having the lower pressure via a second venting port 172.
  • the pin 152b instantly interfacing with the higher pressure fluid acts as a check valve.
  • first and second holes 132a and 132b, and cavities 134a and 134b are formed in the floating ring 160 such that the outer rotor 112 is forcibly positioned against the inner rotor 14 at the in-mesh position 92.
  • the floating ring 160 is substantially balanced in the orthogonal direction.
  • the first and second sets of pins 152a and 152b again act to keep delivery fluid from mixing with the inlet fluid.
  • forces otherwise imposed upon the hydrodynamic bearing have been reduced.
  • the outwardly and inwardly extending lobes 16 and 20 of the inner and outer rotors 14 and 112 are held tightly in mesh at the in-mesh position 92 whereat there is almost no relative motion between them and only passive contact elsewhere.
  • this method comprises the steps of implementing radial passages in the outer rotor of a gerotor set, implementing fluid commutation ports interdicting only the radial passages, and utilizing movement of the radial passages over the ends of the fluid commutation ports for switching pumping chamber fluid connection from one fluid commutation port to the other.
  • an alternate improved method for supporting a gerotor set 102 positioned in a laterally located and roll oriented floating ring such as floating ring 104 or 160 in a gerotor pump configured similarly to gerotor pump 100 or 150 has been enabled by either of the first or second alternate preferred embodiments of the present invention. As depicted in Fig.
  • this method comprises the steps of: conveying fluid pressure instantly representative of that in each of pumping chambers 36 radially outward to the edges of the juxtaposed portions of space 78 between an outer rotor 112 of a gerotor set 102 and floating rings 104 or 160; conveying fluid pressures representative of the pumping chambers 36 generally positioned, on either side of the gerotor set 102 to respective sides of a gerotor pocket of a gerotor pump 100 or 150; applying the higher valued one of the fluid pressures over a selected portion of the in-mesh end 124 of the floating ring 104 or 160 and the lower valued one of the pressures over a selected portion of the out-of-mesh end 126 of the floating ring 104 or 160, thereby applying a force to the floating ring 104 or 160 along the eccentricity axis 54 toward the gerotor set's in-mesh position 92; and hydrostatically coupling that force to the space 78 between the floating ring 104 or 160 and an outer rotor 112 whereby

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne des pompes du type gérotor comprenant des anneaux dansants contraints latéralement (22), ce qui permet d'obtenir un degré de liberté orthogonal et permet aux ensembles de type gérotor (12) positionnés dans lesdites pompes de déterminer leur propre orientation d'engrènement préférée. Par ailleurs, le rotor extérieur de l'ensemble de type gérotor est positionné de force contre le rotor intérieur de l'ensemble de type gérotor dans la position d'engrènement de ce dernier, le mouvement relatif entre les rotors intérieur (14) et extérieur étant ainsi faible. On obtient ainsi un effet d'engrènement sensiblement sans usure et sans frottement de l'ensemble du type gérotor.
PCT/US2004/002778 2004-01-30 2004-01-30 Pompes de type gerotor perfectionnees Ceased WO2005080755A1 (fr)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2013069144A1 (ja) * 2011-11-10 2015-04-02 トヨタ自動車株式会社 車両用内接歯車式オイルポンプ

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4976595A (en) * 1988-03-31 1990-12-11 Suzuki Jidosha Kogyo Kabushiki Kaisha Trochoid pump with radial clearances between the inner and outer rotors and between the outer rotor and the housing
US6419469B1 (en) * 1999-09-22 2002-07-16 Dana Automotive Limited Pump having a main outlet communicating with a secondary outlet by a gap
US6568930B2 (en) * 2000-09-27 2003-05-27 Robert Bosch Gmbh Internal gear pump having a radial adjustment

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4976595A (en) * 1988-03-31 1990-12-11 Suzuki Jidosha Kogyo Kabushiki Kaisha Trochoid pump with radial clearances between the inner and outer rotors and between the outer rotor and the housing
US6419469B1 (en) * 1999-09-22 2002-07-16 Dana Automotive Limited Pump having a main outlet communicating with a secondary outlet by a gap
US6568930B2 (en) * 2000-09-27 2003-05-27 Robert Bosch Gmbh Internal gear pump having a radial adjustment

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2013069144A1 (ja) * 2011-11-10 2015-04-02 トヨタ自動車株式会社 車両用内接歯車式オイルポンプ

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