US3619093A - Gear-type hydraulic machine - Google Patents

Gear-type hydraulic machine Download PDF

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Publication number
US3619093A
US3619093A US876370A US3619093DA US3619093A US 3619093 A US3619093 A US 3619093A US 876370 A US876370 A US 876370A US 3619093D A US3619093D A US 3619093DA US 3619093 A US3619093 A US 3619093A
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Prior art keywords
gear
teeth
type hydraulic
improvement
hydraulic machine
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Expired - Lifetime
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US876370A
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English (en)
Inventor
Hermann Harle
Siegfried Eisenmann
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FURSTLICH HOHENZOLLERNSCHE HUTTENVERWATTUNG LAUCHERTHAL
HOHENZOLLERN HUETTENVERWALT
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HOHENZOLLERN HUETTENVERWALT
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Priority claimed from DE19681809445 external-priority patent/DE1809445C3/de
Application filed by HOHENZOLLERN HUETTENVERWALT filed Critical HOHENZOLLERN HUETTENVERWALT
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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
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/08—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the rotational speed
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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

Definitions

  • a gear-type hydraulic machine wherein fluid is conveyed between gear teeth of two mating gearwheels, includes an internal gear rotatably mounted in the machine and a smaller inner external gear mounted in the machine on journals and meshing with the internal gear.
  • the pressure and the suction sides formed between the cooperating gear teeth are separated exclusively by the mating or meshing teeth.
  • the numbers of teeth of the two gears differ suffieiently that a substantial part of the gear peripheries run out of engagement to define a crescent-shaped zone between the gears.
  • This crescent-shaped zone communicates, through suitably dimensioned leakage passages or gaps, with the respective pressure and suction sides of the machine in order for intermediate pressure to build up in the crescent-shaped zone.
  • This intermediate pressure operates to reduce substantiaily the radial thrust applied to the smaller inner gear by the pressure on the pressure side.
  • FIGA A first figure.
  • Gear-type hydraulic machines wherein a fluid is conveyed between the gear teeth of two mating gears, of which one is an internal gear rotatably mounted in the machine and the other is a smaller inner external gear mounted in the machine on journals, are well known in the art. They are low-pressure pumps, which are built normally for pressure heads not exceeding l atmospheres gauge. In these pumps, the teeth of the internal gear are circular arcuate teeth, and the inner gear has one tooth less than the outer gear.
  • the pressure heads which can be generated by such pumps are not very high because, at a point diametrically opposite the point where the pitch circles of the inner and outer gears meet, the suction and pressure sides of the machine are separated exclusively by the clearance between the crest of one tooth of the inner gear and the crest of one tooth of the outer gear.
  • pumps of this type which are high-pressure pumps, intended to generate pressure heads of 100 atmospheric gauge and more, remains satisfactory for as long as there is no wear. However, apart from wear being liable to occur, these pumps also have other drawbacks.
  • the production cost of such machines is fairly high because the filling member must be machined very precisely.
  • this member is intended to cooperate with the ground tooth crests of the inner and outer gears in the addendum cylinders of the gears. Increasing wear of the filling member causes a considerable reduction in the pumping efficiency of such pumps.
  • This invention relates to gear-type hydraulic machines and, more particularly, to a gear-type hydraulic machine wherein the fluid is conveyed between the teeth of a rotatably mounted internal ring gear in a smaller diameter inner external gear, with the pressure and suction sides between the cooperating gear teeth of the two gears separated exclusively by the mating teeth.
  • the invention is directed to a gear-type hydraulic machine of this kind which is economical to produce, which is free of the above-mentioned disadvantages, which can be used as a high-pressure gear pump of simple design, and which is capable of being so constructed that pressure fluctuations of the fluid delivered by the pump are low for this kind of pump.
  • the gear-type hydraulic machine is so designed that the thrust of the high-pressure fluid, which applies a one-sided bending moment to the shaft of the inner gear, is compensated by the generation of a counterthrust.
  • the machine is designed to be suitable for highpressure operation, for operation with a wide range of speeds, or for both.
  • a gear-type hydraulic machine of the mentioned kind is so designed that the numbers of teeth of the two gears differ sufficiently that a substantial part of the peripheries of the two gears when out of engagement with each other, defining a crescent-shaped zone, between the gears, in which the gear teeth are not in meshing engagement.
  • This zone communicates, through suitably designed leakage gaps or passages, with the pressure and suction sides, respectively, to develop an intermediate pressure in the crescent-shaped zone, this intermediate pressure operating substantially to reduce the radial thrust effective on the inner gear due to the pressure existing on the pressure side.
  • the inlet and outlet ports for the fluid which are provided at least in one and preferably only in one of the sidewalls between which the gears revolve, should be as close to the point of contact of the pitch circles of the gears as the creation of a satisfactorily separating seal will permit.
  • these ports should, in principle, extend far enough for a pumping chamber, between two teeth on the inner gear and two teeth of the outer gear, not to open after having passed across the entry port until this chamber has ceased to be in communication with the port. Conversely, the same applies on the side of the outlet port.
  • this thrust which is generated by a relatively low pressure acting within a relatively large angular region, can be made to compensate exactly that component, of the first above-mentioned radial thrust generated on the pressure side, which is directed radially inwardly from the point of contact of the two pitch circles.
  • the total inward thrust acting on the inner wheel thus can be reduced by as much as about 30 to 40 percent.
  • Another advantage of the invention construction is that the forces acting on the internal gear likewise can be partly compensated. However, this effect on the internal gear is of secondary importance, because the internal gear can be supported around its entire periphery so that its specific hearing pressure is relatively low.
  • the arrangement may be such that the inlet and outlet regions, i.e. the angular regions occupied by the suction and pressure ports, are separated in the peripheral direction by at least a half tooth division from the point of pitch circle contact, and that at least one of these regions extends peripherally to a point that is slightly less than one tooth division away from the point where the two gears run out of or into engagement.
  • This form of construction ensures that a fluid-filled chamber, between two neighboring teeth of the internal gear and two teeth of the inner gear, will open already into communication with the crescent-shaped zone while it still slightly overlaps the end of the relative inlet and/or outlet port. The leakage thus can be determined exactly by choosing the degree of this overlap.
  • the required leakage naturally can be created also by suitably designing the gear teeth. However, this is more difficult to do.
  • the wall which contains the inlet and the outlet ports is arranged to be angularly slightly adjustable, the intermediate pressure can be controlled by appropriate adjustment which permits the overlap on the lowor high-pressure side to be increased and the other reduced, or the two overlaps to be made equal on both sides.
  • the pressure in the crescent-shaped zone can be regulated according to the requirements of the design by increasing or reducing the leakage at the suction or pressure side until this pressure is of the desired magnitude.
  • the gear-type hydraulic machine according to the invention can be operated to function as a hydraulic motor, it is primarily intended to work as a gear pump. ln this case the pressure side is that at the outlet port and the suction side is at the inlet port. The intermediate pressure zone then will extend between these two sides.
  • a gear-type machine according to the invention is arranged to be reversible. This can be done by designing the chamber in which the two meshing gears revolve, including the inlet and outlet ports, so that the layout is symmetrical about a plane containing the axes of rotation of the two gears.
  • Another major advantage of the proposed tooth profile is that the gaps between neighboring teeth are relatively large, in other words that the fluid-filled space available between two teeth on the internal gear and two teeth of the inner gear is relatively large. This, in turn, permits a finer circular pitch to be used, and nonuniformity of flow of the delivered fluid to be substantially diminished.
  • Another advantage of the proposed tooth profile is that during the displacement of the fluid trapped between the gear teeth as these come into mesh, there is no wide tooth crest abruptly penetrating into the fluid to displace a relatively large volume but only the sharp edge at the tip enters the fluid.
  • Yet another advantage of the proposed tooth profile is that it permits a wider choice of the difference between the numbers of teeth on the internal and inner gears.
  • the tooth flanks may meet at the tip at an angle between and 140.
  • An angle between 100 and 1 10 is preferred.
  • lt is also preferred that the relatively remote flanks of two neighboring teeth should form parts of the same circular cylinder surface.
  • the radius of the circle defining the curvatures of the internal gear teeth may with advantage be about 75 percent to 90 percent, preferably between 80 percent and percent, of the radius of the addendum circle of the internal gear.
  • the height of the teeth of the internal gear may with advantage be equal to about half the pitch of the internal gear teeth.
  • the width of the gaps between the teeth at the roots of the teeth of the internal gear should be about 40 percent to 60 percent of the thickness of the roots of the teeth.
  • the profile of the teeth of the inner gear is preferably generated by rolling the inner gear on the internal gear.
  • Such an inner gear may with advantage be produced by first providing a correctly shaped mold and then sintering the gear.
  • the inner gear may be produced with the aid of a suitable gear-cutting machine of the nongenerating shaping or of the generating type.
  • the inner gear also may be produced by hobbing and honing on a machine using the generating roll principle.
  • the internal gear preferably may have only one or two teeth more than the inner gear.
  • the fluid forced through the clearances between the side faces of the gears, the side face of the casing and the side face of a thrust member is collected in annular grooves in the casing, thrust member or both.
  • the collected fluid is then conducted through bores in the casing or in the thrust member or in both, and partly also axially through bores in the gears, and supplied at limited pressure to hydrostatic bearing surfaces or to collecting pockets associated with hydrodynamic bearings, or to both, the fluid being conducted to the hydrodynamic bearings alone if only hydrodynamic bearings are provided.
  • the thrust member has the form of a plate which is urged by fluid pressure against one face of each of the gears.
  • ports and intermediate zone areas defined by O-rings for biasing the thrust member against the sides of the gears, are pressurized through axial ducts traversing the thrust member and communicating with the working chambers, the ports, or the crescent-shaped intermediate zone, respectively, with which these areas are axially aligned.
  • An object of the invention is to provide an improved geartype hydraulic machine wherein a fluid is conveyed between teeth of two mating gears including an internal ring gear and a smaller diameter external gear and wherein the pressure and suction sides between the meshing gear teeth are separated exclusively by the meshing teeth.
  • Another object of the invention is to provide such a machine which is economical to produce and which can be used as a high-pressure gear pump of simple design.
  • a further object of the invention is to provide such a machine in which pressure fluctuations of the fluid delivered by the pump are low.
  • Another object of the invention is to provide such a machine in which the thrust of the high-pressure fluid, applying a bending moment to the shaft of the inner gear, is compensated by the generation of a counter thrust.
  • a further object of the invention is to provide such a machine which is suitable for high-pressure operation, for operation within a wide range of angular velocities, or both.
  • Another object of the invention is to provide such a machine in which the teeth of the internal ring gear have a novel profile.
  • FIG. 1 is a pump according to the invention shown in a section taken on the line A-A in FIG. 2;
  • FIG. 2 is a pump according to the invention shown in a sec tion taken on the line DD in FIG. 1;
  • FIG. 3 is a pump according to the invention shown in a section taken on the line 8-8 in FIG. 2;
  • FIG. 4 is a fragmentary section taken on the line CC in FIG. 2;
  • FIG. 5 is a pump according to the invention showing a preferred gear tooth profile.
  • FIG. 5 An internal ring gear 51 which revolves about a center at 50 meshes with the external teeth of a smaller diameter inner external gear 53 which revolves about a center at 52.
  • the illustrated internal ring gear has eleven internal teeth 54, whereas the inner gear 53 has nine external teeth 55.
  • the inlet and outlet ports 56 and 57, in the illustrated embodiment, are located, symmetrically with reference to a symmetry plane containing the two centers 52 and 50, in one sidewall of a chamber containing the two gears.
  • flanks of the teeth 54 of the internal gear 51 form parts of cylinder surfaces having the same radius r.
  • the teeth are so disposed and designed that the relatively remote flanks of each pair of adjacent teeth form parts of the same cylinder surface. In the sectional drawing, these flanks appear as arcs of a common circle.
  • the height h of the teeth, the thickness 8 of the roots of the teeth and the width b of the clearance gaps between the roots of adjacent teeth of the internal gear are marked in the drawing.
  • the pitch 1 of the teeth is likewise shown.
  • the pitch of the teeth is understood to be the distance between similar points on adjacent teeth, for instance, in the present case, between the crests of the teeth if these were assumed to be a gearwheel of infinite diameter. In practice, in an internal gear, this distance can be measured on the pitch circle, as indicated in FIG. 5.
  • an internal ring gear 2 is rotatably mounted within casing l, with the external peripheral surface of ring gear 2 providing radial location thereof.
  • An inner gear 3, having external teeth, is rotatably mounted in casing l and is axially located therein by means of its side faces.
  • Gear 3 is radially located by a stub axle l7 journaled in a bearing in casing I and the stub axle 9 journaled in a bearing in a thrust member 12.
  • the external peripheral surface of the thrust member 12 preferably has the same overall diameter as the outer diameter of internal ring gear 2.
  • Thrust member 12 is axially displaceable within casing l, but cannot rotate therein. The axial movement of thrust member 12 is limited by a cover 13 facing the outer surface of thrust member 12 and threadedly secured to casing 1 to form a tight seal with the latter.
  • a torsionally elastic drive shaft 16 is secured to rotate with inner gear 3, being connected to the latter by a gear coupling 19 and stub shaft 17.
  • Shaft 16 is rotatably supported in cover 13, as by antifriction bearings 14, for example, which are externally sealed by sealing means 15 surrounding shaft 16.
  • the involute gear teeth which are shown in FIGS. 1 through 4 as an alternative to the previously described preferred type of gear teeth, are provided with slight tip relief in such a way that, within the entire region of tooth engagement between the points of intersection 4, 4', of the addendum circles, the clearance between the tooth flanks is only 0.02 to 0.05 mm.
  • the ports 5 and 5 through which the pumped fluid enters or leaves, in accordance with the direction of rotation, are located in the sidewall of casing 1.
  • gears are cylinder gears of considerable axial length, for handling large volumes, or if the gear diameters are small.
  • the external periphery of internal ring gear 2 is mounted in a bearing recess in casing l, and the stub shafts of inner external gear 3 are mounted in bearing recesses in casing l and thrust bearing l2, respectively.
  • the bearing recesses form two hydrodynamic bearing surfaces 26 separated by an interposed hydrostatic bearing surface 29 communicating with ducts 27 through bores 28.
  • This fluid also enters partly through axial bores 7 and 8 in the gears, and is thus conducted at limited pressure to hydrostatic bearing surfaces 29, 36, or into pockets 43 (FIG. 4), when only hydrodynamic bearings are used.
  • This limited pressure may be controlled by a pressure regulating valve 42 in casing l, valve 42 comprising a plunger 39 which, when necessary, uncovers an outlet opening 40 against the bias of a spring 41.
  • This limited pressure also may be admitted into areas 22 on the outer surface of thrust member 12, for generating axial thrust on thrust member 12, the areas 22 being defined and tightly sealed by the O-rings 241.
  • the pressure-generating areas are pressurized through axial bores 23 traversing thrust member 12, to transmit the pressures existing in working chambers or ports and 5, or the intermediate zone that are in axial alignment with the corresponding thrust-generating areas.
  • the improvement claimed in claim I in which the fluid inlet and fluid outlet regions are separated peripherally, by at least a half tooth division, from the point where the pitch circles of said two gears make contact; at least one of said fluid inlet and fluid outlet regions extending peripherally, in a direction away from said point, to a point that is spaced slightly less than one tooth division from the adjacent peripheral end of said crescent-shaped zone.
  • the improvement claimed in claim 1 including a casing in which said gears are rotatably mounted, said casing having a sidewall member engaging corresponding first sides of said gears; a thrust member mounted in said casing and engaging corresponding second sides of said gears; at least one of said members being formed with annular grooves communicating with the clearances at the side faces of said gears, to collect fluid forced into said clearances; said casing and said thrust member having bearing recesses defining, with said gears, hydraulic bearing recesses; ducts communicating with said hydraulic recesses; and bores connecting said annular grooves to said ducts to supply the collected fluid to said hydraulic bearing recesses at a limited pressure.

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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)
US876370A 1968-11-18 1969-11-13 Gear-type hydraulic machine Expired - Lifetime US3619093A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19681809445 DE1809445C3 (de) 1968-11-18 Zahnradpumpe oder -motor

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US3619093A true US3619093A (en) 1971-11-09

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US876370A Expired - Lifetime US3619093A (en) 1968-11-18 1969-11-13 Gear-type hydraulic machine

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US (1) US3619093A (de)
AT (2) AT291775B (de)
BE (1) BE740909A (de)
CA (1) CA924577A (de)
CH (1) CH503906A (de)
DK (1) DK135433B (de)
FR (1) FR2023513A1 (de)
GB (1) GB1292825A (de)
NL (1) NL162457C (de)
SE (1) SE355844B (de)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3907470A (en) * 1971-08-19 1975-09-23 Hohenzollern Huettenverwalt Gear machine
US4361419A (en) * 1978-08-08 1982-11-30 Volksbank-Raiffeisenbank Buhl E.G. Gerotor liquid pump mounted on a support bushing
US4398874A (en) * 1980-07-10 1983-08-16 Siegfried Eisenmann Gear ring pump
WO1985000202A1 (en) * 1983-06-29 1985-01-17 Peter Norton Plural hydraulic pump system with automatic displacement control
US4717320A (en) * 1978-05-26 1988-01-05 White Hollis Newcomb Jun Gerotor motor balancing plate
US4760759A (en) * 1986-04-15 1988-08-02 Blake William L Geared ratio coupling
US4813853A (en) * 1986-07-19 1989-03-21 Barmag Ag Internal gear pump
US4916899A (en) * 1987-10-30 1990-04-17 Nissan Motor Co., Ltd. Stator shaft connection through oil pump of automatic transmission
US5228289A (en) * 1983-06-29 1993-07-20 Peter Norton Plural hydraulic pump system with unloading valve
US20080031759A1 (en) * 2006-08-04 2008-02-07 Thomas Friedrich Hydraulic rotary motor
EP1882855A3 (de) * 2006-07-25 2008-04-30 Kinshofer GmbH Hydraulischer Drehmotor
US20080187450A1 (en) * 2005-02-16 2008-08-07 Liavas Vasilios B Crescent Gear Pump with Novel Rotor Set
EP3492715A1 (de) * 2017-11-29 2019-06-05 Airbus Helicopters Verbrennungsmotor, der mindestens ein motorgehäuse vom typ mit trockenschmierung umfasst
CN109869240A (zh) * 2017-12-01 2019-06-11 空客直升机 具有至少一个干式油底壳型曲柄箱的内燃发动机
US10577990B2 (en) 2016-10-17 2020-03-03 Airbus Helicopters Internal combustion engine having at least one crankcase of the dry-sump type

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2943948A1 (de) 1979-10-31 1981-05-27 G.L. Rexroth Gmbh, 8770 Lohr Hydrostatische zahnradmaschine
US8535030B2 (en) * 2010-02-17 2013-09-17 Kelly Hee Yu Chua Gerotor hydraulic pump with fluid actuated vanes
CN111648957B (zh) * 2020-07-22 2025-04-25 中国石油大学(华东) 一种新型无困液齿轮泵的齿轮转子及其设计方法

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US2124140A (en) * 1935-08-19 1938-07-19 Foster Frank Geden Engine, pump, meter, and the like
US2159720A (en) * 1936-02-27 1939-05-23 Gunnar A Wahlmark Pump
US2547392A (en) * 1946-04-02 1951-04-03 Myron F Hill Continuous contact internal rotor for engines
US2666336A (en) * 1950-06-10 1954-01-19 Hill Myron Francis Internal gear teeth
US3034446A (en) * 1957-09-06 1962-05-15 Robert W Brundage Hydraulic pump or motor
US3188969A (en) * 1957-09-06 1965-06-15 Robert W Brundage Hydraulic pump or motor
US3198127A (en) * 1959-05-19 1965-08-03 Robert W Brundage Hydraulic pump or motor
US3427983A (en) * 1966-05-31 1969-02-18 Robert W Brundage Pressure balanced bearing loads in hydraulic devices

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2124140A (en) * 1935-08-19 1938-07-19 Foster Frank Geden Engine, pump, meter, and the like
US2159720A (en) * 1936-02-27 1939-05-23 Gunnar A Wahlmark Pump
US2547392A (en) * 1946-04-02 1951-04-03 Myron F Hill Continuous contact internal rotor for engines
US2666336A (en) * 1950-06-10 1954-01-19 Hill Myron Francis Internal gear teeth
US3034446A (en) * 1957-09-06 1962-05-15 Robert W Brundage Hydraulic pump or motor
US3188969A (en) * 1957-09-06 1965-06-15 Robert W Brundage Hydraulic pump or motor
US3198127A (en) * 1959-05-19 1965-08-03 Robert W Brundage Hydraulic pump or motor
US3427983A (en) * 1966-05-31 1969-02-18 Robert W Brundage Pressure balanced bearing loads in hydraulic devices

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3907470A (en) * 1971-08-19 1975-09-23 Hohenzollern Huettenverwalt Gear machine
US4717320A (en) * 1978-05-26 1988-01-05 White Hollis Newcomb Jun Gerotor motor balancing plate
US4361419A (en) * 1978-08-08 1982-11-30 Volksbank-Raiffeisenbank Buhl E.G. Gerotor liquid pump mounted on a support bushing
US4398874A (en) * 1980-07-10 1983-08-16 Siegfried Eisenmann Gear ring pump
US4432712A (en) * 1980-07-10 1984-02-21 Siegfried Eisenmann Hydrostatic gear ring machine
US5228289A (en) * 1983-06-29 1993-07-20 Peter Norton Plural hydraulic pump system with unloading valve
WO1985000202A1 (en) * 1983-06-29 1985-01-17 Peter Norton Plural hydraulic pump system with automatic displacement control
US4760759A (en) * 1986-04-15 1988-08-02 Blake William L Geared ratio coupling
US4813853A (en) * 1986-07-19 1989-03-21 Barmag Ag Internal gear pump
US4916899A (en) * 1987-10-30 1990-04-17 Nissan Motor Co., Ltd. Stator shaft connection through oil pump of automatic transmission
US20080187450A1 (en) * 2005-02-16 2008-08-07 Liavas Vasilios B Crescent Gear Pump with Novel Rotor Set
US7766634B2 (en) * 2005-02-16 2010-08-03 Magna Powertrain Inc. Crescent gear pump with novel rotor set
EP1882855A3 (de) * 2006-07-25 2008-04-30 Kinshofer GmbH Hydraulischer Drehmotor
US20080031759A1 (en) * 2006-08-04 2008-02-07 Thomas Friedrich Hydraulic rotary motor
US10577990B2 (en) 2016-10-17 2020-03-03 Airbus Helicopters Internal combustion engine having at least one crankcase of the dry-sump type
EP3492715A1 (de) * 2017-11-29 2019-06-05 Airbus Helicopters Verbrennungsmotor, der mindestens ein motorgehäuse vom typ mit trockenschmierung umfasst
CN109869240A (zh) * 2017-12-01 2019-06-11 空客直升机 具有至少一个干式油底壳型曲柄箱的内燃发动机

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Publication number Publication date
CA924577A (en) 1973-04-17
DK135433C (de) 1977-10-31
DK135433B (da) 1977-04-25
NL162457B (nl) 1979-12-17
GB1292825A (en) 1972-10-11
AT292464B (de) 1971-08-25
CH503906A (de) 1971-02-28
NL162457C (nl) 1980-05-16
NL6917310A (de) 1970-05-20
SE355844B (de) 1973-05-07
AT291775B (de) 1971-07-26
DE1809445A1 (de) 1970-06-04
BE740909A (de) 1970-04-01
FR2023513A1 (de) 1970-08-21
DE1809445B2 (de) 1977-05-12

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