US3270681A - Rotary fluid pressure device - Google Patents

Rotary fluid pressure device Download PDF

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Publication number
US3270681A
US3270681A US412100A US41210064A US3270681A US 3270681 A US3270681 A US 3270681A US 412100 A US412100 A US 412100A US 41210064 A US41210064 A US 41210064A US 3270681 A US3270681 A US 3270681A
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United States
Prior art keywords
members
shaft
valve
fluid
star
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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.)
Expired - Lifetime
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US412100A
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English (en)
Inventor
Lynn L Charlson
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GERMANE CORP
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GERMANE CORP
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Publication date
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Priority to US412100A priority Critical patent/US3270681A/en
Priority to GB31362/65A priority patent/GB1055117A/en
Priority to DE1553057A priority patent/DE1553057C3/de
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Publication of US3270681A publication Critical patent/US3270681A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • 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
    • F04C2/103—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 one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F04C2/104—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 one member having simultaneously a rotational movement about its own axis and an orbital movement having an articulated driving shaft
    • 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
    • F04C2/103—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 one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F04C2/105—Details concerning timing or distribution valves

Definitions

  • This invention relates to rotary fluid pressure motors and pumps of the kind which utilize the type of gear 1 mechanism disclosed in United States Patent No. 1,682,563, issued August 28, 1928, to Myron P. Hill.
  • the mechanism disclosed in the Hill patent is referred to in the art as a gerotor and consists of an internally toothed ring member and an externally toothed star member Which partakes of a hypocycloidal movement and travels in an orbit about the axis of the ring member.
  • An object of the present invention is to provide a rotary fluid pressure motor or pump of the gerotor type having a new and improved valving and drive system.
  • FIG. 1 is a longitudinal sectional view of a rotary fluid pump or motor embodying the invention and taken on line I--I of FIG. 4;
  • FIG. 2 is an end view from the left side of FIG. 1;
  • FIG. 3 is an end view from the right side of FIG. 1;
  • FIG. 4 is a transverse sectional view taken on line IVIV of FIG. 1;
  • FIG. 5 is a transverse sectional view taken on line VV of FIG. 1;
  • FIG. 6 is a fragmentary longitudinal sectional view taken on line VIVI of FIG. 5.
  • a sectional casing comprising a generally cylindrically shaped shaft section 10, a cylindrically shaped gerotor section 12 and a cylindrically shaped valving section 14. These casing sections are held together in axial alignment by a plurality of circumferentially spaced bolts 16.
  • Gerotor section 12 is a generally annularly shaped ring member which has a plurality of internal teeth 18.
  • An externally toothed star member 20, having at least one fewer teeth 22 than ring member 12, is disposed eccentrically in the chamber or space formed and surrounded by ring member 12.
  • Star member is moveable orbitally relative to the ring member 12, the axis 24 of star member 20 being moveable in an orbital path about the axis 26 of ring member 12.
  • the teeth 22 thereof intermesh with the ring member teeth 18 in sealing engagement to form expanding and contracting cells 28 which are equal in number to the number of star member teeth 22.
  • the vertical centerline 30 incidentally represents the line of eccentricity for the star member 20 for that particular position of the star member relative to the ring member 12.
  • the cells 28 on the left side of the line of eccentricity would be expanding and the cells 28 on the right side would be contracting.
  • the device is used as a motor, fluid under pressure is directed to the expanding cells and exhausted from the contracting cells.
  • the device is used as a pump, fluid is sucked into the expanding cells and delivered under pressure from the contracting cells.
  • the valving arrangement which facilitates the pumping or motor action will be described further on herein.
  • the shaft section 10 of the "ice casing for the device has a cylindrically shaped counterbore 32 which is concentric relative to the centerline 26 which is also the centerline for ring member 12.
  • a eylindrically shaped shaft 34 having a stepped portion 36 of smaller diameter is rotatably disposed in the counterbore 32.
  • An annularly shaped plate 37 is provided which is attachable to shaft casing section 10 with a plurality of circumferentially arranged bolts 36 for retaining shaft 34 in its installed position.
  • the stepped portion 36 of the 9 shaft 34 may be driven by an electric motor or the like when the device is utilized as a pump or may drive apparatus such as a boat propeller when the device is utilized as a motor.
  • Shaft 34 and shaft casing section 10 are provided respectively with bores 40 and 42 which are in axial alignment by reason of both bores being concentric relative to the device centerline 26.
  • the inner side of easing section 10 is in abutting engagement with ring member 12 and forms a side for the gerotor chamber.
  • the bore 42 of the casing section 10 must thus be limited in diameter so that cells 28 formed between the teeth of the gerotor star and ring members will be closed by easing section 10 for all orbital positions of the star member 20.
  • Star member 20 has a bore 46 which is concentric relative to the teeth 22 thereof and the centerline 24 when the star member is in the position shown in FIGS. 1 and 4.
  • the left side of the star bore 46 has a plurality of circumferentially arranged, axially extending teeth or splines 48 and the left side of the shaft bore 40 also has a plurality of circumferentially arranged, axially extending teeth or splines 50.
  • An intermediate shaft 52 is disposed in bores 40, 42 and 46 between shaft 34 and star member 20.
  • the left and right ends of shaft 52 have splines 55 and 56 respectively which in each case are circumferentially arranged and extend axially.
  • Splines 55 of shaft 52 are equal in number and mesh with splines 50 of shaft 34 and the same is true at the opposite end of intermediate shaft 52 wherein splines 56 of shaft 52 are equal in number and mesh with splines 48 of star 20.
  • Star member 20 is eccentrically disposed relative to ring member 12, as mentioned above, and intermediate shaft 52 is thus always in cocked or tilted position relative to shaft 3-2, which has the same axis as ring member 12, and the axis of star member 20.
  • a star member having six teeth will make one revolution about its own axis for every six times the star member orbits in the opposite direction about the axis 26 of the ring member 12.
  • the right end of intermediate shaft 52 has both orbital and rotational movement in common with the star member 20 while the left end of shaft 52 has only rotational movement in common with shaft 34.
  • the spline connections between intermediate shaft 52 and shaft 3 4 and between intermediate shaft 52 and star member 20 are forms of universal joints which permit shaft 52 to have the motion described above.
  • star member 20 When the device is utilized as a pump, star member 20 will be gyrated by a turning force applied to shaft 34 and transmitted to star member 20 through intermediate shaft 52. When the device is used as a motor, the force created by the rotation of star member 20 about its own axis 24 will be transmitted through intermediate shaft 52 to shaft 34 to cause turning of shaft 34.
  • the casing valve section 14 has a counterbore 58 which is concentric relative to the axis or centerline 26 and has cylindrically shaped valve 60 rotatably disposed therein.
  • the diameter of valve 60 is at least as large as the diameter of the gerotor chamber formed by the ring member 12 so that the cells 28 formed between the teeth of the gerotor star and ring members will be closed by the radial face 66 of valve 60 for all orbital positions of star member 20.
  • Valve 60 is provided with an eccentrically disposed counterbore 62 which for convenience may have the same diameter as star member bore 46. Counterbore 62 is offset from the axis of rotation 26 of the valve 60 a distance equal to the distance that star member 20 is eccentrically offset relative to ring member 12. Valve 60 is connected to star member 20 by aligning valve counterbore 62 with star member bore 46 and inserting a short shaft 64 in the bore formed by the two bores 46 and 62. Short shaft 64 is rotatably mounted relative to star member 20 and valve 60 and the orbiting of star member 20 will cause valve 60 to rotate in the same direction and at the same speed as the orbiting speed of the star member 20 and vice versa.
  • valve casing member 14 has two radially extending ports 74 and 76 each of which connect the periphery or outer surface of valve casing 14 with the bore 58.
  • Each of the ports 74 and 76 may be an inlet or outlet port depending upon the direction of the rotation of the shaft 34.
  • Port 74 is fluidly connected to recess 70 and port 76 is fluidly connected to recess 72.
  • valve casing 14 The fluid connections between ports 74 and 76 and valve recesses 70 and 72 are formed partly in the valve casing 14 and partly in the valve 60.
  • Two axially spaced annular grooves 78 and 80 are formed in valve casing 14 which are aligned with and communicate with the ports 74 and 76.
  • Two other axially spaced annular grooves 82 and 84 are formed on valve 60 which are axially aligned respectively with the casing grooves 78 and 80 to form two enclosed annular passages.
  • Channels 86 and 88 are provided in valve 60 which respectively connect groove 82 and port 76 to the valve recess 70 and groove 84 and port 76 to valve recess 72.
  • the rotary fluid pressure device may be utilized as either a pump by connecting one of the ports 74 or 76 to a source of fluid and rotating the shaft 34 in the correct direction or as a motor by connecting one of the ports 74 or 76 to a source of fluid pressure and connecting shaft 34 to a mechanical device desired to be driven.
  • a relatively slow speed imparted to shaft 34 will cause relatively rapid orbiting of star member 20 and result in a high fluid delivery rate.
  • the shaft 34 makes one rotation for every six orbiting cycles of the star member 20, in a case where star member has six teeth, and as a result the shaft 34 produces a relatively high torque at a relatively slow speed.
  • fluid inlet and outlet means an internally toothed ring member defining the outer wall of a chamber, a cooperating externally toothed star member disposed eccentrically in said chamber, one of said members being capable of orbital movement about the axis of the other of said members with the teeth of said members intermeshing in sealing engagement to form expanding cells on one side of the line of eccentricity and contracting cells on the other side of said line during relative movement between said members, one of said members being rotatable about its own axis relative to said other member at a slower speed than said orbital movement during relative rotation between said members, valve means operatively connected to the orbiting one of said members so that its rotational speed is the same as the orbiting speed of said one of said members, said valve means defining fluid passage means which com prise fluid supply means only on one side thereof in communication with said fluid inlet means and fluid exhausting means only on the other side thereof in communication with said fluid outlet means, said valve means being indexed with reference to the position of said star member relative to said ring
  • a fluid pressure device as defined in claim 1 having a body portion attached to said ring member for receiving said fluid inlet and outlet means.
  • a fluid pressure device as defined in claim 4 in which said star member has one less tooth than said ring member.
  • a fluid pressure device as defined in claim 3 in which said body portion defines a bore having a first annular groove communicating with said inlet means and a second annular groove axially spaced from said first annular groove communicating with said outlet means, said valve means being rotatably disposed in said bore with said fluid supply and exhaust means thereof being in respective communication with said annular grooves, said fluid supply and exhaust means being formed on diametrically opposite sides of said valve means in the form of crescent shaped recesses.
  • connection between said intermediate shaft and said one of said members is a universal joint comprising groove and abutment means and the connection between said intermediate shaft and said drive shaft is a universal joint comprising groove and abutment means.
  • fluid inlet and outlet means an internally toothed ring member defining the outer wall of a chamber, a cooperating externally toothed star member disposed eccentrically in said chamber and being capable of orbital movement about the axis of said ring member, the teeth of said members intermeshing in sealing engagement to form expanding cells on one side of the line of eccentricity and contracting cells on the other side of said line during relative movement between said members, said star member being rotatable about its own axis in the opposite direction and at a slower rate of speed than said orbital movement during relative rotation between said members, valve means operatively coupled to said star member so that the rotational speed of said valve means is the same as the orbiting speed of said star member, said valve means defining fluid passages which comprise fluid supply means only one one side thereof in communication with said fluid inlet means and fluid exhausting means only on the other side thereof in communication with said fluid outlet means, said valve means being indexed with reference to the position of said star member relative to said ring member so that upon rotation of said valve
  • a fluid pressure device as defined in claim 8 in which said ring member is stationary.
  • a fluid pressure device as defined in claim 8 having a body portion attached to said ring member for receiving said fluid inlet and outlet means.
  • a fluid pressure device as defined in claim 8 in which said star member has fewer teeth than said ring member.
  • a fluid pressure device as defined in claim 10 in which said body portion defines a bore having a first annular groove communicating with said inlet means and a second annular groove axially spaced from said first annular groove communicating with said outlet means, said valve means being rotatably disposed in said bore with said fluid supply and exhaust means thereof being in respective communication with said annular grooves, said fluid supply and exhaust means being formed on diametrically opposite sides of said valve means in the form of crescent shaped recesses.
  • connection between said intermediate shaft and said star member is a universal joint comprising groove and abutment means and the connection between said intermediate shaft and said drive shaft is a universal joint comprising groove and abutment means.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
US412100A 1964-11-18 1964-11-18 Rotary fluid pressure device Expired - Lifetime US3270681A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US412100A US3270681A (en) 1964-11-18 1964-11-18 Rotary fluid pressure device
GB31362/65A GB1055117A (en) 1964-11-18 1965-07-22 Rotary fluid pressure pump or motor
DE1553057A DE1553057C3 (de) 1964-11-18 1965-08-05 Rotationskolbenmaschine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US412100A US3270681A (en) 1964-11-18 1964-11-18 Rotary fluid pressure device

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US3270681A true US3270681A (en) 1966-09-06

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DE (1) DE1553057C3 (de)
GB (1) GB1055117A (de)

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3309999A (en) * 1965-06-21 1967-03-21 Char Lynn Co Drive mechanism for gerotor gear set
US3316814A (en) * 1965-04-22 1967-05-02 Germane Corp Rotary fluid pressure device
US3348493A (en) * 1965-10-21 1967-10-24 Char Lynn Co Fluid pressure remote control devices and systems
US3367239A (en) * 1964-07-28 1968-02-06 Takagi Moriyuki Fluid reducers
US3401602A (en) * 1965-06-09 1968-09-17 J.C. Birdwell Pressure fluid operated motor or the like
US3446153A (en) * 1967-07-17 1969-05-27 Wayne B Easton Fluid pressure operated motor or pump
US3453966A (en) * 1967-05-04 1969-07-08 Reliance Electric & Eng Co Hydraulic motor or pump device
US3494255A (en) * 1968-01-12 1970-02-10 Lamina Inc Through-flow rotary-piston hydraulic motor
US3549283A (en) * 1969-02-18 1970-12-22 George V Woodling Axial limit means for male and female spline teeth in a fluid pressure device
US3680987A (en) * 1969-06-19 1972-08-01 Danfoss As Rotary piston engine
US3826596A (en) * 1972-04-26 1974-07-30 Danfoss As Rotary piston machine with splined internal shaft
US4316707A (en) * 1977-11-22 1982-02-23 Danfoss A/S Gerotor with valve plate attached to rotor
EP0394821A2 (de) * 1989-04-24 1990-10-31 Eaton Corporation Verteilerventil für eine innenachsige Kreiskolbenmaschine
US5211551A (en) * 1992-09-10 1993-05-18 Eaton Corporation Modular motor
US6033195A (en) * 1998-01-23 2000-03-07 Eaton Corporation Gerotor motor and improved spool valve therefor
US6572353B2 (en) * 2000-11-17 2003-06-03 Sauer-Danfoss Holding A/S Hydraulic gerotor motor having a valve plate adjacent the toothed wheel
US20040089496A1 (en) * 2002-11-08 2004-05-13 Nacco Materials Handling Group, Inc. Integrated hydraulic control system
US6783339B2 (en) 2002-04-24 2004-08-31 Parker Hannifin Corporation Hydraulic motor with a separate spool valve
WO2005061897A1 (en) * 2003-12-20 2005-07-07 Sauer-Danfoss Aps Hydraulic motor

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1682563A (en) * 1921-11-05 1928-08-28 Myron F Hill Internal rotor
US2132812A (en) * 1933-04-28 1938-10-11 Gunnar A Wahlmark Rotary engine
US2758573A (en) * 1954-12-20 1956-08-14 Krozal William Gear type hydraulic unit
USRE25126E (en) * 1958-11-25 1962-02-20 Controller for fluid pressure operated devices
USRE25291E (en) * 1956-06-08 1962-12-04 Fluid pressure device and valve
US3087436A (en) * 1960-12-02 1963-04-30 Ross Gear And Tool Company Inc Hydraulic pump

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2871831A (en) * 1959-02-03 Internal gear machines
US1389189A (en) * 1919-06-10 1921-08-30 Feuerheerd Ernest Rotary motor or pump
DE416850C (de) * 1921-02-11 1925-07-30 Alois Herrmann Maschine mit im Gehaeuse sich abwaelzendem und gleitendem Kolben von unrundem und eckigem Querschnitt
US2339966A (en) * 1939-08-16 1944-01-25 Equi Flow Inc Internal gear pump
US2417701A (en) * 1944-07-17 1947-03-18 John B Parsons Compensating device for rotary pumps

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1682563A (en) * 1921-11-05 1928-08-28 Myron F Hill Internal rotor
US2132812A (en) * 1933-04-28 1938-10-11 Gunnar A Wahlmark Rotary engine
US2758573A (en) * 1954-12-20 1956-08-14 Krozal William Gear type hydraulic unit
USRE25291E (en) * 1956-06-08 1962-12-04 Fluid pressure device and valve
USRE25126E (en) * 1958-11-25 1962-02-20 Controller for fluid pressure operated devices
US3087436A (en) * 1960-12-02 1963-04-30 Ross Gear And Tool Company Inc Hydraulic pump

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3367239A (en) * 1964-07-28 1968-02-06 Takagi Moriyuki Fluid reducers
US3316814A (en) * 1965-04-22 1967-05-02 Germane Corp Rotary fluid pressure device
US3401602A (en) * 1965-06-09 1968-09-17 J.C. Birdwell Pressure fluid operated motor or the like
US3309999A (en) * 1965-06-21 1967-03-21 Char Lynn Co Drive mechanism for gerotor gear set
US3348493A (en) * 1965-10-21 1967-10-24 Char Lynn Co Fluid pressure remote control devices and systems
US3453966A (en) * 1967-05-04 1969-07-08 Reliance Electric & Eng Co Hydraulic motor or pump device
US3446153A (en) * 1967-07-17 1969-05-27 Wayne B Easton Fluid pressure operated motor or pump
US3494255A (en) * 1968-01-12 1970-02-10 Lamina Inc Through-flow rotary-piston hydraulic motor
US3549283A (en) * 1969-02-18 1970-12-22 George V Woodling Axial limit means for male and female spline teeth in a fluid pressure device
US3680987A (en) * 1969-06-19 1972-08-01 Danfoss As Rotary piston engine
US3826596A (en) * 1972-04-26 1974-07-30 Danfoss As Rotary piston machine with splined internal shaft
US4316707A (en) * 1977-11-22 1982-02-23 Danfoss A/S Gerotor with valve plate attached to rotor
EP0394821A2 (de) * 1989-04-24 1990-10-31 Eaton Corporation Verteilerventil für eine innenachsige Kreiskolbenmaschine
US4992034A (en) * 1989-04-24 1991-02-12 Eaton Corporation Low-speed, high-torque gerotor motor and improved valving therefor
EP0394821A3 (de) * 1989-04-24 1991-07-10 Eaton Corporation Verteilerventil für eine innenachsige Kreiskolbenmaschine
US5211551A (en) * 1992-09-10 1993-05-18 Eaton Corporation Modular motor
US6033195A (en) * 1998-01-23 2000-03-07 Eaton Corporation Gerotor motor and improved spool valve therefor
US6572353B2 (en) * 2000-11-17 2003-06-03 Sauer-Danfoss Holding A/S Hydraulic gerotor motor having a valve plate adjacent the toothed wheel
US6783339B2 (en) 2002-04-24 2004-08-31 Parker Hannifin Corporation Hydraulic motor with a separate spool valve
US20040089496A1 (en) * 2002-11-08 2004-05-13 Nacco Materials Handling Group, Inc. Integrated hydraulic control system
US7036625B2 (en) 2002-11-08 2006-05-02 Nmhg Oregon, Inc. Integrated hydraulic control system
US20060169521A1 (en) * 2002-11-08 2006-08-03 Nacco Materials Handling Group, Inc. Integrated hydraulic control system
US7699135B2 (en) * 2002-11-08 2010-04-20 Nmhg Oregon, Llc Integrated hydraulic control system
WO2005061897A1 (en) * 2003-12-20 2005-07-07 Sauer-Danfoss Aps Hydraulic motor

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Publication number Publication date
DE1553057B2 (de) 1981-07-02
DE1553057A1 (de) 1970-07-16
GB1055117A (en) 1967-01-18
DE1553057C3 (de) 1983-04-28

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