US3059432A - Axial piston hydraulic units - Google Patents

Axial piston hydraulic units Download PDF

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Publication number
US3059432A
US3059432A US4138A US413860A US3059432A US 3059432 A US3059432 A US 3059432A US 4138 A US4138 A US 4138A US 413860 A US413860 A US 413860A US 3059432 A US3059432 A US 3059432A
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Prior art keywords
cylinder block
shaft
plate
axial piston
casing
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Expired - Lifetime
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US4138A
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English (en)
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Thoma Hans
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/0052—Cylinder barrel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0035—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/0055—Valve means, e.g. valve plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/0064—Machine housing
    • F01B3/0067—Machine housing cylinder barrel bearing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/007—Swash plate
    • F01B3/0073—Swash plate swash plate bearing means or driving or driven axis bearing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0082—Details
    • F01B3/0094—Driving or driven means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/10—Control of working-fluid admission or discharge peculiar thereto
    • F01B3/103—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block
    • F01B3/106—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block by changing the inclination of the swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
    • F16H39/04—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit
    • F16H39/06—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type
    • F16H39/08—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type each with one main shaft and provided with pistons reciprocating in cylinders
    • F16H39/10—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type each with one main shaft and provided with pistons reciprocating in cylinders with cylinders arranged around, and parallel or approximately parallel to the main axis of the gearing
    • F16H39/14—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of the same type each with one main shaft and provided with pistons reciprocating in cylinders with cylinders arranged around, and parallel or approximately parallel to the main axis of the gearing with cylinders carried in rotary cylinder blocks or cylinder-bearing members

Definitions

  • the invention therefore specifically relates to certain improvements in hydraulic units of a type which can also be termed swashplate motor or pump units.
  • Such improved units include axially disposed pistons having integral therewith or permanently connected thereto a spherical head which is engaged in a complementary-shaped socket on a slipper that bears against a preferably nonrotatable inclined plane or plate, generally referred to in the art as a swashplate.
  • the lateral forces produced by the pressure of the pistons against the inclined plate are transmitted by the rigid or solid pistons back to the cylinder block and from there to a drive shaft.
  • the fluid flow to and from the axially disposed cylinders is via a non-rotating control or timing plate formed with Generally, the segmentally-shaped inlet and delivery ports are in alignment with the piston accommodating bores or cylinders.
  • one object of the present invention to provide an improved structural relationship of such axial piston hydraulic units in which the ports through which fluid flows to and from the cylinders are offset from the pitch circle of the cylinder block toward the axis of rotation thereof so as to thereby substantially reduce leakage and other losses.
  • the mounting or suspension for such plate transmits forces to the plate to overcome the pressure reaction between the timing plate and the cylinder block due to the surface of the delivery ports.
  • This mounting also produces a certain excess of pressure that urges the timing plate into intimate contact with the cylinder block. This excess pressure acts on the timing plate at least approximately close to its symmetrical axis so as to avoid large tilting moments between the timing plate and the adjacent face of the cylinder block.
  • -It is a further specific object to provide an axial piston hydraulic unit which includes a stiff or rigid drive shaft relationship resulting in a minimum noise level and in which such drive shaft is mounted or suspended at one or both ends in plural bearings capable of transmitting bending moments.
  • FIGURE 1 is a view partly in elevation and partly in longitudinal cross-section of an axial piston unit of the invention
  • FIGURE 2 is a similar view taken at right angles to the relationship of FIGURE 1 and showing the unit of the invention with the parts in a different position,
  • FIGURE 3 is a view partly in elevation and partly in longitudinal cross-section illustrating the combination of two axial piston units with a gearing and in which the two units and gearing are disposed coaxially in casing means,
  • FIGURE 4 is a plan view of that face of the timing plate remote from the cylinder block
  • FIGURE 5 is a cross-sectional view on an enlarged scale illustrating a part of a timing plate
  • FIGURE 6 is a plan view of the face of the timing plate opposite to that shown in FIGURE 4, and
  • FIGURE 7 is a cross-sectional view taken along line 77 of FIGURE 6.
  • the unit of FIGURES 1 and 2 includes a casing structure C which includes apertured end closures C and C and within which is mounted a cylinder block 1 rigidly keyed by key means K to a drive shaft 8.
  • the cylinder block 1 is provided with a plurality of axially disposed piston accommodating bores or cylinders 1%.
  • pistons 2 which have at one end a spherical head 3 that is either integral with each piston or is permanently connected thereto.
  • the spherical heads of the pistons 2 are mounted in complementary-shaped sockets formed in slippers 4 which are in engagement with the inclined plate 5 connected to the substantially semi-cylindrically-shaped member 6.
  • the outer surface of this member is engaged in an arcuate surface at one end of the casing as shown in FIGURE 2.
  • the inclination of the plate 5 can be varied by turning the shaft '7, FIGURE 1.
  • the shaft 7 is an adjusting shaft and carries on its inner end a lever 7 having a tongue 7" that fits in a bore in the member 6 so that when shaft '7 is turned the member 6 is displaced to vary the inclination of plate 5.
  • Bearings 9, 10 and 11 rigidly support the drive shaft within the casing.
  • the inlet and delivery flow of liquid to the cylinders is via a non-rotating control or timing plate 14 having segmentally-shaped admission and delivery openings 22 and 23 which communicate with ports 25 in the cylinder block that lead fluid to and from the respective cylinders, see FIGURE 6.
  • a non-rotating control or timing plate 14 having segmentally-shaped admission and delivery openings 22 and 23 which communicate with ports 25 in the cylinder block that lead fluid to and from the respective cylinders, see FIGURE 6.
  • the upper ends of the admission and delivery ports that is, the openings at the surface of the timing plate and the adjacent ends of the ports in the cylinder block are offset from the pitch circle of the cylinders toward the axis of rotation or the axis of symmetry of the unit.
  • This offsetting provides important advantages, namely, it has a tendency to reduce leakage and pressure losses because the cross-sectional area of the segmental admission and delivery ports and the fluid ports in the cylinder block can be made larger for a given total surface area under pressure. While this relationship might lead to the disadvantage that considerable tilting moments are generated in the cylinder block, because the reactions of the piston forces are no longer in alignment with the pressure reactions through the cylinder ports, this advantage is overcome by rigidly keying the cylinder block to the drive shaft so as to in effect carry away this tilting moment. The other load the drive shaft has to carry is derived from the side or lateral forces generated by the pistons bearing against the inclined plate 5.
  • the invention provides two balancing pistons 18 preferably located closer to the axis than the bushings. Further, the balancing pistons are preferably offset longitudinally from the bushings. These balancing pistons are provided with pre-loading springs 17 and are connected by conduits 3t), FIGURES 6 and 7, to the inlet and delivery ports 22 and 23. In FIGURE 7 is shown the provision of annular chamber 2% incorporated around a balancing piston 13%. In FIGURE is illustrated a suitable check valve 300 provided in the conduit 301 connecting the space that accommodates the balancing piston with the delivery port 23.
  • the reaction between the casing and the timing plate can be controlled so as to overcome the reaction forces due to the i pressure field between the timing plate and the end face of thecylinder block and to provide an excess force acting approximately centrally of the timing plate to urge it into contact with the cylinder block. Since it will be generally necessary to provide a certain amount of excess force on the timing plate acting in a direction toward the cylinder block in order to, with certainty, overcome pulsating piston forces, it is preferable to locate a pressure fed axial bearing 12 and 13 between the timing plate and the cylinder block. The structure and nature of this relationship is more clearly shown in my prior US. Patent No. 2,916,334, dated December 8, 1961.
  • FIGURE 3 shows the preferred embodiment of the application of two axial piston units ofthe invention in a hydrostatic transmission having a split power ar-
  • the relationship includes a two-part in the differential gear which feeds the power to the output shaft.
  • the arrangement further includes a clutch means 68 which when operated, clutches the hollow shaft 65 to the output shaft 63, thereby introducing a direct mechanical transmission ratio of l to 1.
  • This relation ship is of advantage, particularly in some vehicular applications of the invention.
  • the shaft 10 is connected to the engine of the vehicle by any suitable means known in the art.
  • the adjustability of the angle ofinclination of the swashplates against which the slippers bear, and thus the variation in the stroke of the pistons can be con- 7 trolled by turning shafts 70, 7d.
  • both of these shafts are mounted in a pair of conical roller bearings.
  • the bearings for shaft 65 are shown at 67, and shaft 10 is mounted in similarly shaped bearings 67 shown at the upper part of FIGURE 3.
  • Each pair of roller bearings provides a mounting or suspension which is capable of absorbing bending moments.
  • the transmission further includes a brake 80 of any suitable type such as a band brake.
  • a brake 80 of any suitable type such as a band brake.
  • this brake is loose or not applied so as to permit proper operation of the transmission.
  • the application of the brake will effect the connection between the input and output shafts.
  • the clutch 63 in FIGURE 3 can establish a direct drive and permit bypassing of the transmission and can also avoid losses due to oil pressure or circulation problems upon suitable adjustment of the piston strokes in the pump and motor, respectively.
  • the unit including cylinder block 1 is a primary unit modates two coaxially arranged axial piston units whereas 7 the lower casing part accommodates a gearing relationship and an output shaft.
  • the two axial piston units include cylinder blocks 1, 1 arranged coaxially with the associated timing plates 14, 14- arranged adjacent to one another so there is only a common set of bushings 15', 16 which transmit the oil directly from one timing plate to the other. Both timing plates are mounted for slight adjustable movement relative to the ring members 50, 51 on the interior of the casing part 53, While pins or bolts 81 and 82 prevent rotation of these timing plates.
  • the input shaft 10 that is keyed to the cylinder block -1 is elongated and has a squared end fitting in a similarly shaped aperture in a bevel gear of a known dilferential gear relationship.
  • the drive shaft that is keyed to cylinder block 1 is hollow and surrounds input shaft It
  • a bevel gear 64 is formed on or fixed to the end of hollow drive shaft 65 and bevel gears 61 mounted in a cage 62 are in mesh with gears 69, 64 and the cage is connected to the output shaft 63.
  • This relationship operates in a'known manner to provide a split power arrangement where a part of the power is transmitted mechanical- ,ly, another part hydraulically and both parts combined and operates as an hydraulic pump, being connected by input shaft 10 to a'prime mover such as an internal combustion engine in a vehicle or an electric motor in some other application.
  • the unit including the connecting block 1' is a secondary unit and functions as an hydraulic motor.
  • the piston strokes of both units can be varied'by turning the adjusting shafts and 71.
  • the clutch or coupling 68 may be operated either mechanically or by means of oil pressure and arranged to connect the input and output shafts directly or indirectly using the split power transmission or gearing shown in FIGURE 3.
  • An axial piston hydraulic unit including a casing, a rotatable cylinder block within the casing, said cylinder blockhaving a plurality of piston-accommodating bores therein, apiston reciprocably disposed in each bore and including an exposed outer end, a rotatable shaft, means 4 rigidly connecting said shaft to the cylinder block, a
  • swashplate cooperable with the exposed outer ends of said pistons, means for disposing said swashplate at an angle to the axis of said shaft for translating rotary motion of said shaft into reciprocable movements of the pistons and vice versa
  • said cylinder block having an end face constituting a distribution end, ports communicating with said end'face and with said bores, a control plate adjacent said end face of the cylinder block, said control plate having segmentally-shaped fiuid admission and delivery ports therein terminating in the face of the control plate adjacent the said end face of the cylinder block, means mounting the control plate in the casing for slight adjusting movement relative to the casing and cylinder block so as to maintain tight contact between the adjacent faces of the cylinder block and control plate; the adjacent communicating ends of the ports in the cylinder block and the admission and delivery ports being oifset from the pitch circle of said bores in a direction toward the axis of rotation of the cylinder block and the tilting moments acting on the cylinder block being absorbed by said shaft.
  • An axial piston hydraulic unit as claimed in claim 1 in which means are operatively associated with the control plate for transmitting forces between the control plate and the casing comprising balancing pistons mounted within the control plate and means for feeding oil thereto from at least one of said admission and said delivery ports so as to equalize pressure reactions between the cylinder block and control plate.
  • An hydraulic transmission including a casing, two axial piston hydraulic units within the casing and constituting primary and secondary units respectively, said primary unit constituting an hydraulic pump and including a shaft adapted for connection to a prime mover and constituting the input shaft of the transmission, said input shaft being elongated to provide an extension, said secondary unit constituting an oil motor and including a hollow shaft surrounding the extension of the input shaft and constituting an output shaft, said primary unit including a rotatable cylinder block having a plurality of piston-accommodating bores therein, a piston reciprocably disposed in each bore and including an exposed outer end, means rigidly connecting the cylinder block to said input shaft, a swashplate for cooperation with the outer ends of the pistons, means for disposing said swashplate at an angle to the axis of said input shaft for translating rotary motion of the input shaft into reciprocal movements of the pistons and vice versa, said cylinder block having an end face constituting a distribution end, said block further having ports therein communicating between said end face and said piston-acco
  • secondary unit of said transmission comprising a similar cylinder block, means rigidly connecting said last-mentioned cylinder block to said hollow shaft, said second cylinder block having piston-accommodating bores therein, pistons in said bores terminating in exposed outer ends projecting from the face of said second cylinder block remote from said first cylinder block, a second swashplate for cooperation with the exposed ends of the pistons in the second cylinder block, means for disposing said second swashplate at an angle to the axis of said hollow shaft for translating reciprocal movements of the pistons into rotary motion of the hollow shaft and vice versa, said second cylinder block having ports therein providing communication between the piston-accommodating bores of said second block and the end face of such second block adjacent the first block, a second control plate within the casing similar to the first control plate and having similarly arranged admission and delivery ports therein, means mounting said second control plate coaxially with and adjacent to the first-mentioned control plate for slight adjusting movement between the respective control plates, the casing and said second

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Motor Power Transmission Devices (AREA)
  • Control Of Fluid Gearings (AREA)
  • Reciprocating Pumps (AREA)
US4138A 1962-05-08 1960-01-22 Axial piston hydraulic units Expired - Lifetime US3059432A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR896791A FR1321353A (fr) 1962-05-08 1962-05-08 Pompe ou moteur hydraulique à pistons

Publications (1)

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US3059432A true US3059432A (en) 1962-10-23

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US4138A Expired - Lifetime US3059432A (en) 1962-05-08 1960-01-22 Axial piston hydraulic units

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US (1) US3059432A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
FR (1) FR1321353A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
GB (1) GB895805A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
NL (1) NL278180A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3175511A (en) * 1963-05-23 1965-03-30 Lucas Industries Ltd Hydraulic pumps or motors
US3183846A (en) * 1962-12-03 1965-05-18 Lucas Industries Ltd Fluid pumps and motors
US3200762A (en) * 1962-12-19 1965-08-17 Unipat Ag Axial piston pumps or motors
US3230893A (en) * 1961-05-31 1966-01-25 Sundstrand Corp Swashplate pump
US3255673A (en) * 1962-10-09 1966-06-14 Thoma Hans Axial piston hydraulic units
US3596568A (en) * 1968-10-14 1971-08-03 Deere & Co Fluid-translating apparatus
US3625253A (en) * 1968-12-05 1971-12-07 Von Roll Ag Hydraulic unit
US4142450A (en) * 1976-01-13 1979-03-06 Thoma Jean U Axial piston rotary hydraulic machines
DE2904342A1 (de) * 1978-02-06 1979-08-09 Samuel Shiber Hydrostatisches getriebe
US4196587A (en) * 1978-02-06 1980-04-08 Samuel Shiber Multi-mode transmission
US4196586A (en) * 1978-02-06 1980-04-08 Samuel Shiber Multi-mode hydrostatic transmission
DE4035748A1 (de) * 1989-11-09 1991-05-16 Vickers Systems Gmbh Axialkolbenpumpe fuer hohe drehzahlen
US11236736B2 (en) * 2019-09-27 2022-02-01 Honeywell International Inc. Axial piston pump with port plate having balance feed aperture relief feature
US12305457B1 (en) * 2024-01-08 2025-05-20 Halliburton Energy Services, Inc. Downhole tractor drive module

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1453552B1 (de) * 1962-12-06 1970-03-12 Lucas Industries Ltd Dichtung zwischen Steuerspiegelscheibe und Gehäuse einer Schiefscheiben-Axialkolbenmaschine
DE102012016056A1 (de) * 2012-08-14 2014-02-20 Robert Bosch Gmbh Steuerplatte und Gehäuseteil für hydrostatische Maschine und Verfahren zur Montage einer hydrostatischen Maschine
DE102016115904B4 (de) * 2015-08-27 2017-12-07 Denso Corporation Anlasser für Maschine

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2569562A (en) * 1946-06-03 1951-10-02 Froebe Douglas Fitch Pump and motor hydraulic transmission
US2679139A (en) * 1951-10-12 1954-05-25 Chester A Posson Variable speed rotary pump and motor transmission
US2803112A (en) * 1951-12-04 1957-08-20 Sundstrand Machine Tool Co Control means for constant speed hydraulic pump and motor transmission

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2569562A (en) * 1946-06-03 1951-10-02 Froebe Douglas Fitch Pump and motor hydraulic transmission
US2679139A (en) * 1951-10-12 1954-05-25 Chester A Posson Variable speed rotary pump and motor transmission
US2803112A (en) * 1951-12-04 1957-08-20 Sundstrand Machine Tool Co Control means for constant speed hydraulic pump and motor transmission

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3230893A (en) * 1961-05-31 1966-01-25 Sundstrand Corp Swashplate pump
US3255673A (en) * 1962-10-09 1966-06-14 Thoma Hans Axial piston hydraulic units
US3183846A (en) * 1962-12-03 1965-05-18 Lucas Industries Ltd Fluid pumps and motors
US3200762A (en) * 1962-12-19 1965-08-17 Unipat Ag Axial piston pumps or motors
US3175511A (en) * 1963-05-23 1965-03-30 Lucas Industries Ltd Hydraulic pumps or motors
US3596568A (en) * 1968-10-14 1971-08-03 Deere & Co Fluid-translating apparatus
US3625253A (en) * 1968-12-05 1971-12-07 Von Roll Ag Hydraulic unit
US4142450A (en) * 1976-01-13 1979-03-06 Thoma Jean U Axial piston rotary hydraulic machines
DE2904342A1 (de) * 1978-02-06 1979-08-09 Samuel Shiber Hydrostatisches getriebe
US4196587A (en) * 1978-02-06 1980-04-08 Samuel Shiber Multi-mode transmission
US4196586A (en) * 1978-02-06 1980-04-08 Samuel Shiber Multi-mode hydrostatic transmission
DE4035748A1 (de) * 1989-11-09 1991-05-16 Vickers Systems Gmbh Axialkolbenpumpe fuer hohe drehzahlen
US11236736B2 (en) * 2019-09-27 2022-02-01 Honeywell International Inc. Axial piston pump with port plate having balance feed aperture relief feature
US12305457B1 (en) * 2024-01-08 2025-05-20 Halliburton Energy Services, Inc. Downhole tractor drive module

Also Published As

Publication number Publication date
GB895805A (en) 1962-05-09
FR1321353A (fr) 1963-03-15
NL278180A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)

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