US3289602A - Fluid pressure device - Google Patents

Fluid pressure device Download PDF

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Publication number
US3289602A
US3289602A US484918A US48491865A US3289602A US 3289602 A US3289602 A US 3289602A US 484918 A US484918 A US 484918A US 48491865 A US48491865 A US 48491865A US 3289602 A US3289602 A US 3289602A
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United States
Prior art keywords
gear
gears
pump
stator
recesses
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.)
Expired - Lifetime
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US484918A
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English (en)
Inventor
Bernard C Hudgens
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.)
Northrop Grumman Space and Mission Systems Corp
Original Assignee
TRW Inc
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 TRW Inc filed Critical TRW Inc
Priority to US484918A priority Critical patent/US3289602A/en
Priority to FR42961A priority patent/FR1460428A/fr
Priority to SE16565/65A priority patent/SE315204B/xx
Priority to DE1553238A priority patent/DE1553238B2/de
Priority to DK122466AA priority patent/DK117677B/da
Application granted granted Critical
Publication of US3289602A publication Critical patent/US3289602A/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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

Definitions

  • This invention relates to a fluid pressure device, including a pump or a motor and more particularly deals with p a hydraulic pump or motor of the internal gear type wherein the outer gear has one more tooth than the inner gear and one of the gears orbits about the axis of the other gear when it is rotated about its own axis and wherein the teeth or lobes of one of the gears are individual units accommodating wide tolerance variations and automatically sealed relative to the gear body under the influence of hydraulic pressure developed between the gears.
  • tion may take the form of rollers, shoes, or the like in-
  • the segment receiving recesses are larger than the segments to permit movement of the segments relative to the gear body, but at least a portion of the recess walls are adapted to be "mated with the segments to provide a good sealing engagement of the segments with the gear body.
  • the coacting lsealing surfaces of the segments and gear body can be shifted to accommodate wide tolerance variations and wear of the parts in use.
  • the segments can be provided with hardened surfaces to resist wear while the gear body carrying the segments can be composed of a less hardened high strength metal which is easy to machine.
  • the invention will hereinafter be specifically described as embodied in an internal gear pump having an orbiting rotor embraced by a stator where the rotor is driven through a wobble stick connection with the drive shaft and a driven cylindrical valve surrounding the wobble stick controls fluid flow through the pump. It will be understood, however. that the principles of this invention are generally applicable to fluid pressure devices embodying internal gear sets.
  • the illustrated device is especially useful in power steering linkages for controlling the power steering motor from a steering wheel. The invention is not limited to the hereinafter described specifically illustrated embodiment.
  • Another object of the invention is to provide a fluid pressure device with an internal gear set having the lobes lot:
  • Another object of the invention is to provide vanes on the enveloping stator of an internal gear set, which vanes will accommodate wide tolerance variations in the manufacture of the gear set and will create their own seals under the influence of pressure developed by the device.
  • a specific object of this invention is to provide the stator of an internal gear pump of the type having an orbiting rotor with individual lobes shiftable in the stator into proper operating positions regardless of wear developed between the gears.
  • Another specific object of this invention is to provide an internal gear pump with a stator having recesses carrying cylindrical rollers in loose-fit relation for engaging the teeth of an orbiting rotor.
  • Another specific object of the invention is to provide an internal gear pump or motor of the type having an orbiting rotor surrounded by a stator wherein the stator teeth are composed of individual vanes shiftable into proper operating positions under the action of the rotor and pressures developed between the rotor and stator.
  • FIGURE 1 is a longitudinal cross-sectional view with parts in elevation of a fluid pressure device especially adapted for power steering usage and incorporating the features of this invention; 7
  • FIGURE 2 is a transverse sectional view taken generally along the line II-II of FIGURE 1;
  • FIGURE 3 is a transverse sectional view taken generally along the broken line III-III of FIGURE 1;
  • FIGURE 4 is a View similar to FIGURE 2, but illustrating the direction of rotor force on the individual shiftable stator lobes; t i
  • FIGURE 5 is an enlarged fragmentary view of a portion of FIGURE 4 illustrating the manner in which the pressure differential across the vane or tooth segment creates the seal;
  • FIGURE 6 is a View similar to FIGURE 5, but illustrating a modified vane construction.
  • the present invention as mentioned hereinabove relates to the new and improved means for sealing between the rot-or element and stator gear element of the internal gear set which is utilized in a hydraulic device.
  • a hydraulic device In order to properly describe the environment within which the present invention resides, it is necessary to discuss to some length the construction of the hydraulic device. To this end, the device illustrated, particularly in FIGURES 1, 2 and 3, will be described as a pump with those skilled in the art readily recognizing the interchangeability of the device to function as a motor.
  • the pump which has been shown comprises a housing 10 which receives a drive shaft 11 through a bore therein which shaft can be driven by any appropriate means.
  • the pump elements are located in the housing opposite the shaft 11 or at the left end of FIGURE 1, and'these elements comprise an outer fixed stator gear element 12 and an inner rotatable rotor element 13 together forming the internal gear set. These two elements are located between a wear plate 14 on the left end of the housing 10 and a cover 15 suitably held in position by screws 16 threaded into the left end of the housing.
  • a commutating valve spool 20 is rotatably located in the bore of the housing between the shaft 11 and the pump elements and through this valve spool extends a shaft or wobble stick 21 which transmits the rotation of shaft 11 to the rotor element 13. It will be apparent from reviewing FIGURES l and 2 that the connection between the one end of shaft 21 and the end of shaft 11 amounts to a universal joint connection as well as the connection of the other end of shaft 21 to the rotor element. The purpose of these connections is to permit the rotor element 13 to partake of its rotational and orbiting movement which will be discussed in more detail hereinafter.
  • the rotor element is formed with teeth 23, in this embodiment specifically six in number, and the stator gear element carries one more tooth, sometimes referred to as lobes 25, in this embodiment specifically seven in number.
  • the rotor element has an axis indicated by the point 26 in FIGURE 2 and the stator element has an axis indicated by the point 28.
  • Rotation of the shaft 11 in an appropriate direction will cause the rotor to rotate about its own axis 26 in the direction of arrow 29 (FIGURE 2).
  • the rotor axis 26 will orbit about the stator axis 28 in the opposite direction or in the direction of arrow 30.
  • the result of this action is to cause the pockets 32 formed between the stator lobes 25 to pass through alternately contracting pressure cycles or strokes and expanding intake or suction strokes.
  • the rotor axis will orbit about the stator axis six times for each complete rotation of shaft 11, and each orbit will produce seven pressure pulses or strokes.
  • At any one instant of time there are 3+ pockets undergoing an exhaust or pressure stage and 3+ pockets in the intake or suction stage.
  • One revolution of the drive shaft will therefore produce six orbits or 42 pump or pressure pulses.
  • the shaft 11 has been connected to the commutating valve sleeve 20 by way of a drive pin 33 which projects from the valve sleeve into one end of a slot 34 in the left end 35 of the drive shaft. This causes the commutating valve spool 20, the rotor element 13, and the drive shaft 11 to travel at substantially the same rotational speed.
  • the bore of the housing is provided with two annular grooves 38 and 39 which communicate respectively with radial passages 40 and 41 opening in the sides of the housing 10 and adapted for connection to conduits through which the fluid enters and leaves the pump.
  • the groove 38 is located in the plane of the slot 34 and therefore is in constant communication with the interior of the com-mutating valve spool 20 while the groove 39 is located within the axial limits of the valve spool 20.
  • a circumferential series of ports 43 extend at one end to the :bore of the housing and at the other end through holes 45 in the wear plate 14 to the pockets 32 between the lobes of the stator gear element 12.
  • the commutating valve spool is provided with a plurality of circumferentially spaced radial passages 47, (further identified by letters a, b, c, a, e, and j) which extend from the outer surface thereof to the hollow inside, and located between these radial passages 47 are provided corresponding numbers of axially extending grooves 49 (further identified by letters a, b, c, d, e and 7). These grooves 49 extend axially a length suflicient to provide a fluid bridge between the ports 43 and the annular groove 39 when the grooves 49 and ports 43 are in axial alignment with each other.
  • FIGURES 1, 2 and 3 show the sectional views shown 4 in FIGURES 2 and 3 show the rotor element and the commutating valve spool in the same angular position they occupy relative to each other because of their mechanical connection with the drive shaft 11.
  • FIGURE 2 shows that pockets A, B and C are on an intake stroke, pockets D, E and F are on a pressure stroke, and pocket G is at the point of completing a pressure stroke and just prior to starting an intake stroke.
  • the pockets A, B and C are being connected in FIGURE 3 to the fluid input side of the pump through radial passages a, b and 0, whereas pockets D, E and F communicate with the pressure or output side of the pump by way of axial grooves d, e and f, whereas pocket G is in what may be referred to as a transition position being neither connected to the radial passage 1 or axial groove a. From this description it will be apparent how the rotating and orbiting rotor element produces successively alternating pump and intake strokes in the various pockets 32 and how the action of the commutating valve spool appropriately connects the pockets undergoing pump strokes to the pressure side of the pump and at the same time connects the expanding pockets undergoing an intake stroke to the intake side of the pump.
  • the tooth which is undergoing the intake stroke may be immediately behind the tooth producing the pump stroke or it may be the second or third tooth behind depending upon which tooth is taken as the reference tooth, because as described hereinabove, at least three pump pulses are being produced and at least three intake pulses.
  • the improvement of the present invention comprises a vane or individual tooth for each of the seven lobes of the stator 12.
  • these vanes or tooth segments 50 take the form of hollow cylindrical metal tubes each receiving a screw 16 therethrough and each fitting in a somewhat oversized fragmental cylindrical recess 51 in the stator body.
  • the recesses 51 open inwardly to accommodate projection of the tubes 50 to form the lobes 25.
  • the tubes 50 extend the full distance between the wear plate 14 and the end cover 15, but they have a sliding fit with the cover and wear plate at their ends so that they can rotate and shift radially in the recesses 51.
  • the sliding fit between the ends of the tubes or rollers and the wear plate and end cover is such that leakage will be minimized.
  • the stator 12 therefore, comprises, as shown in FIGURE 4, a metal ring or apertured disk 52 with a ring of fragmental cylindrical recesses 51 spaced equally around the inner periphery thereof and loosely receiving the rollers or tubes 50 therein.
  • This ring or disk 52 has finger-like portions 53 between each of the recesses 51 providing gaps between the rollers 50 for receiving the stator teeth 23.
  • About one-third of the periphery of each roller 50 extends inwardly from the recesses 51 to provide the active lobe surfaces 25 for the stator.
  • the main or controlling force vector on the rollers is created by the pressure differential between the successive pockets of the pump.
  • the pocket C is the last intake pocket before the pressure cycle starts with the successive pocket D.
  • Pocket D is thus under greater pressure than pocket C and this pressure differential across the vane roller 50 urges the vane into sealing contact with the tooth 23 at point 60 and with the recess 51 at point 61.
  • the general direction of the loading force on the roller vane 50 is indicated by the arrow 62. leakage from the high pressure pocket D back to the lower pressure pocket C is thus effectively prevented even thoughthe roller vane 50 is loosely fitted in its recess 51 of the stator body 52.
  • the loose tooth segments or roller vanes are automatically positioned in their free-fitting recesses under the forces developed within the pump and the assembly in effect is self-compensating. If wear develop-s on the rollers or on the teeth of the rotor, this self-compensating action will still maintain the efliciency of the pump and leakage paths will not be opened up. In addition, friction of operation can be somewhat reduced because the rollers 50 can shift and rotate to some degree under the influence of the rotor.
  • the modified stator 12 has a ring body 52, provided with rectangular recesses 51' around its inner periphery receiving gear segments or vanes 50' of generally rectangular configuration, but having rounded lobe defining inner faces 25'.
  • the segments 50' can be solid or hollow as desired, and as shown in FIGURE 6, the screws 16' are relocated to pass through the ring body 52' between the recesses 51 thereof.
  • the vanes 50 function in the same manner as the roller vanes 50 and are sealed under influence of the pressure differential between pockets C and D at points 60' and 61 with the general direction of the sealing force being indicated by the arrow 62'.
  • the segments or vanes 50' do not rotate in the recesses or pockets 51' as do the rollers 50, but otherwise function in the same manner as the rollers 50.
  • this invention provides an internal gear pump or motor with an internal gear set having vanes, lobes, or tooth segments loosely carried by the enveloping gear of the set to greatly increase permissible tolerances in the set and to provide a self-compensating, self-sealing assembly.
  • the invention materially decreases the manufacturing costs of pumps and motors of the internal gear type especially where one of the gear elements orbits as it rotates.
  • an internal gear type fluid pressure device includ ing a first gear surrounded by and meshed with a second gear, one of said gears having one less tooth than the other gear, said gears being relatively rotatable, one of said gears being mounted for orbital movement relative to the other gear, said second gear having circumferentially spaced fragmental cylindrical recesses around the inner periphery thereof opening through said inner periphery, cylindrical rollers mounted in said recesses and free to rotate therein, said rollers projecting beyond said openings through the inner periphery of the second gear to provide the teeth for said second gear, said first gear and a portion of the second gear between the rollers cooperating with the rollers to form expanding and contracting chambers therebetween, said first gear simultaneously contacting at least two rollers in all positions of the gears to form seals, two of said seals separating the expanding chambers from the contracting chambers, .and passages communicating with the chambers for flow of fluid into the expanding chambers and out of the contracting chambers.
  • an internal gear type fluid pressure device including a first gear surrounded by and meshed with a second gear, one of said gears having one less tooth than the other gear, said gears being relatively rotatable, one of said gears being mounted for orbital movement relative to the other gear, said second gear having circumferentially spaced recesses around the inner periphery thereof separated by fingers therebetween and opening through said inner periphery, individual gear teeth vane units loosely mounted in said recesses and projecting therefrom to define the tooth contact surfaces of the second gear, said first gear and the fingers of the second gear cooperating with the vane units to form expanding and contracting chambers therebetween, said first gear simultaneously contacting at least two of the vane units in all positions of the gears to form seals, two of said seals separating the expanding chambers from the contracting chambers, passages communicating with the chambers between the gears for flow of fluid into and out of the chambers, and said vane units being shiftable under the influence of pressure developed in the chambers to seek sealed engagement with the gears regardless
  • a fluid pressure device of the internal-external orbiting gear type which comprises a housing having a fluid inlet and a fluid outlet, a shaft rotatably supported in the housing, a first gear, a second gear surrounding and meshed with the first gear, one of said gears having one less tooth than the other gear, said gears being relatively rotatable, one of said gears orbiting about the axis of the other gear and coacting therewith to form expanding and contracting chambers between the gears, means coupling said shaft to a rotatable gear, said orbiting gear orbiting about the axis of the other gear at a higher speed than the shaft speed, ports communicating with the charmbers between the gears, a valve in the housing controlling flow between the ports and the fluid inlet and outlet of the housing, said second gear having circumferentially spaced recesses therearound opening through the inner periphery thereof, individual gear teeth vane units loosely positioned in said recesses and projecting beyond the openings in the inner periphery of the second gear to define
  • the device of claim 1 including a valve controlling flow through the passages.
  • the device of claim 6 including a shaft coupled to a rotatable gear.
  • valve is cou pled t the shaft.
  • valve is a cylindrical spool valve and a wobble stick extends through the valve to couple the shaft with the orbiting gear.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Hydraulic Motors (AREA)
US484918A 1965-09-03 1965-09-03 Fluid pressure device Expired - Lifetime US3289602A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US484918A US3289602A (en) 1965-09-03 1965-09-03 Fluid pressure device
FR42961A FR1460428A (fr) 1965-09-03 1965-12-20 Pompe ou moteur à pression de fluide
SE16565/65A SE315204B (da) 1965-09-03 1965-12-21
DE1553238A DE1553238B2 (de) 1965-09-03 1966-01-07 Rotationskolbenmaschine
DK122466AA DK117677B (da) 1965-09-03 1966-03-09 Tandhjulspumpe eller -motor.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US484918A US3289602A (en) 1965-09-03 1965-09-03 Fluid pressure device

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US3289602A true US3289602A (en) 1966-12-06

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US484918A Expired - Lifetime US3289602A (en) 1965-09-03 1965-09-03 Fluid pressure device

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US (1) US3289602A (da)
DE (1) DE1553238B2 (da)
DK (1) DK117677B (da)
FR (1) FR1460428A (da)
SE (1) SE315204B (da)

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3352247A (en) * 1965-12-08 1967-11-14 Char Lynn Co Fluid pressure device with dual feed and exhaust
US3460481A (en) * 1967-09-27 1969-08-12 Trw Inc Rotor-stator gear set in a hydraulic motor-pump device
US3473438A (en) * 1966-08-05 1969-10-21 Danfoss As Loading compensated commutating valve for fluid motors and pumps
DE1934467A1 (de) * 1968-08-29 1971-02-11 Trw Inc Rotor-Statorradsatz fuer Arbeitsmaschinen
US3591320A (en) * 1969-04-08 1971-07-06 George V Woodling Pressurized roller means in a fluid pressure device
US3601513A (en) * 1969-07-22 1971-08-24 Trw Inc Hydraulic device
US3614274A (en) * 1969-06-19 1971-10-19 Danfoss As Hydraulic rotary piston machine
US3619089A (en) * 1970-03-13 1971-11-09 Automatic Radio Mfg Co Fluid-pressure device
US3623829A (en) * 1969-11-12 1971-11-30 Nichols Co W H Internal gear set
DE1653823B1 (de) * 1967-12-23 1972-05-04 Danfoss As Rotationskolbenmaschine fuer fluessige Medien
US3692439A (en) * 1971-02-03 1972-09-19 George V Woodling Fluid pressure responsive mechanism in a fluid pressure device
DE2221183A1 (de) * 1972-04-29 1973-11-08 Zahnradfabrik Friedrichshafen Hydraulikpumpe oder -motor, insbesondere fuer hydrostatische lenkeinrichtungen von kraftfahrzeugen
US3910733A (en) * 1969-09-18 1975-10-07 Leslie H Grove Rotary mechanism having at least two camming elements
US3915603A (en) * 1973-05-03 1975-10-28 Eaton Corp Radial balancing means with sealing vanes for a hydraulic device
US3979167A (en) * 1975-01-27 1976-09-07 Grove Leslie H Internal gear set having roller teeth
JPS5347367Y1 (da) * 1975-01-20 1978-11-13
US4394112A (en) * 1979-12-17 1983-07-19 Woodling George V Combination roller tooth set having roller teeth and concave surfaces disposed to engage each other
US4457678A (en) * 1982-02-24 1984-07-03 Trw Inc. Fluid drive mechanism
EP0119460A2 (en) * 1983-02-17 1984-09-26 Arthur E. Rineer Hydraulic energy-conversion device
DK153234B (da) * 1976-07-16 1988-06-27 Trw Inc Hydraulisk tandhjulsmaskine af planettypen
US4767292A (en) * 1987-07-20 1988-08-30 Trw Inc. Electrical commutation apparatus
US5145348A (en) * 1991-05-15 1992-09-08 Eaton Corporation Gerotor pump having an improved drive mechanism
US5505597A (en) * 1993-12-06 1996-04-09 White Hydraulics, Inc. Pressure tolerant balanced motor valve
EP0879963A1 (en) * 1997-05-23 1998-11-25 Eaton Corporation Coupling for use with a gerotor device
WO2001046560A1 (en) * 1999-12-20 2001-06-28 Sauer-Danfoss Holding A/S Hydraulic machine
DE19962802A1 (de) * 1999-12-23 2001-07-05 Danfoss Fluid Power As Nordbor Zahnsatz für eine hydraulische Maschine
DE19962804A1 (de) * 1999-12-23 2001-07-05 Danfoss Fluid Power As Nordbor Zahnrad für eine hydraulische Maschine
US6783339B2 (en) 2002-04-24 2004-08-31 Parker Hannifin Corporation Hydraulic motor with a separate spool valve
US20040266538A1 (en) * 2003-06-27 2004-12-30 Khoury Jihad J. Reduced stress rotational coupling and a method of using same

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US211769A (en) * 1879-01-28 Improvement in rotary water-meters
US1341846A (en) * 1918-04-22 1920-06-01 Ellick H Gollings Rotary power device
US2189976A (en) * 1937-01-27 1940-02-13 Lavaud Dimitrl Sensaud De Rotary engine
US2586964A (en) * 1946-09-24 1952-02-26 Jr Frederick Kraissl Rotary pump
US2657638A (en) * 1948-04-12 1953-11-03 Byron Jackson Co Rotary pump
US2672824A (en) * 1944-05-11 1954-03-23 Gerotor May Corp Hydraulic pump or motor
US2821171A (en) * 1956-06-08 1958-01-28 Lynn L Charlson Fluid pressure device and valve
US2975766A (en) * 1958-04-28 1961-03-21 Kelsey Hayes Co Hydraulic rotary actuator with unrestrained vane and seal members
US2988065A (en) * 1958-03-11 1961-06-13 Nsu Motorenwerke Ag Rotary internal combustion engine
US2992616A (en) * 1956-07-02 1961-07-18 Arthur E Rineer Fluid power converter
US3082747A (en) * 1958-01-06 1963-03-26 Borsig Ag Rotary piston engine
US3087436A (en) * 1960-12-02 1963-04-30 Ross Gear And Tool Company Inc Hydraulic pump
US3123012A (en) * 1964-03-03 Hydraulic gear apparatus
US3175503A (en) * 1961-03-31 1965-03-30 Renault Segmentary sealing blades for rotary engines
US3204615A (en) * 1960-11-09 1965-09-07 Bayerische Motoren Werke Ag Rotary piston machine

Patent Citations (15)

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Publication number Priority date Publication date Assignee Title
US3123012A (en) * 1964-03-03 Hydraulic gear apparatus
US211769A (en) * 1879-01-28 Improvement in rotary water-meters
US1341846A (en) * 1918-04-22 1920-06-01 Ellick H Gollings Rotary power device
US2189976A (en) * 1937-01-27 1940-02-13 Lavaud Dimitrl Sensaud De Rotary engine
US2672824A (en) * 1944-05-11 1954-03-23 Gerotor May Corp Hydraulic pump or motor
US2586964A (en) * 1946-09-24 1952-02-26 Jr Frederick Kraissl Rotary pump
US2657638A (en) * 1948-04-12 1953-11-03 Byron Jackson Co Rotary pump
US2821171A (en) * 1956-06-08 1958-01-28 Lynn L Charlson Fluid pressure device and valve
US2992616A (en) * 1956-07-02 1961-07-18 Arthur E Rineer Fluid power converter
US3082747A (en) * 1958-01-06 1963-03-26 Borsig Ag Rotary piston engine
US2988065A (en) * 1958-03-11 1961-06-13 Nsu Motorenwerke Ag Rotary internal combustion engine
US2975766A (en) * 1958-04-28 1961-03-21 Kelsey Hayes Co Hydraulic rotary actuator with unrestrained vane and seal members
US3204615A (en) * 1960-11-09 1965-09-07 Bayerische Motoren Werke Ag Rotary piston machine
US3087436A (en) * 1960-12-02 1963-04-30 Ross Gear And Tool Company Inc Hydraulic pump
US3175503A (en) * 1961-03-31 1965-03-30 Renault Segmentary sealing blades for rotary engines

Cited By (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3352247A (en) * 1965-12-08 1967-11-14 Char Lynn Co Fluid pressure device with dual feed and exhaust
US3473438A (en) * 1966-08-05 1969-10-21 Danfoss As Loading compensated commutating valve for fluid motors and pumps
US3460481A (en) * 1967-09-27 1969-08-12 Trw Inc Rotor-stator gear set in a hydraulic motor-pump device
DE1653922A1 (de) * 1967-09-27 1972-02-10 Trw Inc Arbeitsmaschine wie Pumpe oder Motor
DE1653823B1 (de) * 1967-12-23 1972-05-04 Danfoss As Rotationskolbenmaschine fuer fluessige Medien
DE1934467A1 (de) * 1968-08-29 1971-02-11 Trw Inc Rotor-Statorradsatz fuer Arbeitsmaschinen
US3591320A (en) * 1969-04-08 1971-07-06 George V Woodling Pressurized roller means in a fluid pressure device
US3614274A (en) * 1969-06-19 1971-10-19 Danfoss As Hydraulic rotary piston machine
US3601513A (en) * 1969-07-22 1971-08-24 Trw Inc Hydraulic device
US3910733A (en) * 1969-09-18 1975-10-07 Leslie H Grove Rotary mechanism having at least two camming elements
US3623829A (en) * 1969-11-12 1971-11-30 Nichols Co W H Internal gear set
US3619089A (en) * 1970-03-13 1971-11-09 Automatic Radio Mfg Co Fluid-pressure device
US3692439A (en) * 1971-02-03 1972-09-19 George V Woodling Fluid pressure responsive mechanism in a fluid pressure device
DE2221183A1 (de) * 1972-04-29 1973-11-08 Zahnradfabrik Friedrichshafen Hydraulikpumpe oder -motor, insbesondere fuer hydrostatische lenkeinrichtungen von kraftfahrzeugen
US3915603A (en) * 1973-05-03 1975-10-28 Eaton Corp Radial balancing means with sealing vanes for a hydraulic device
JPS5347367Y1 (da) * 1975-01-20 1978-11-13
US3979167A (en) * 1975-01-27 1976-09-07 Grove Leslie H Internal gear set having roller teeth
DK153234B (da) * 1976-07-16 1988-06-27 Trw Inc Hydraulisk tandhjulsmaskine af planettypen
US4394112A (en) * 1979-12-17 1983-07-19 Woodling George V Combination roller tooth set having roller teeth and concave surfaces disposed to engage each other
US4457678A (en) * 1982-02-24 1984-07-03 Trw Inc. Fluid drive mechanism
EP0119460A3 (en) * 1983-02-17 1984-12-05 Arthur E. Rineer Hydraulic energy-conversion device
EP0119460A2 (en) * 1983-02-17 1984-09-26 Arthur E. Rineer Hydraulic energy-conversion device
US4767292A (en) * 1987-07-20 1988-08-30 Trw Inc. Electrical commutation apparatus
US5145348A (en) * 1991-05-15 1992-09-08 Eaton Corporation Gerotor pump having an improved drive mechanism
US5505597A (en) * 1993-12-06 1996-04-09 White Hydraulics, Inc. Pressure tolerant balanced motor valve
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US6619937B2 (en) 1999-12-20 2003-09-16 Sauer-Danfoss Holding A/S Hydraulic machine
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DE19962802A1 (de) * 1999-12-23 2001-07-05 Danfoss Fluid Power As Nordbor Zahnsatz für eine hydraulische Maschine
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DE19962804C2 (de) * 1999-12-23 2002-02-14 Sauer Danfoss Nordborg As Nord Zahnsatz für eine hydraulische Maschine
US6672854B2 (en) 1999-12-23 2004-01-06 Sauer-Danfoss Holding A/S Tooth set for a hydraulic machine
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US20040266538A1 (en) * 2003-06-27 2004-12-30 Khoury Jihad J. Reduced stress rotational coupling and a method of using same
US7118360B2 (en) * 2003-06-27 2006-10-10 Caterpillar Inc Reduced stress rotational coupling and a method of using same

Also Published As

Publication number Publication date
SE315204B (da) 1969-09-22
FR1460428A (fr) 1966-11-25
DE1553238A1 (de) 1971-04-08
DK117677B (da) 1970-05-19
DE1553238B2 (de) 1974-09-26

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