US3796137A - Rotary hydraulic machines - Google Patents

Rotary hydraulic machines Download PDF

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Publication number
US3796137A
US3796137A US00224134A US3796137DA US3796137A US 3796137 A US3796137 A US 3796137A US 00224134 A US00224134 A US 00224134A US 3796137D A US3796137D A US 3796137DA US 3796137 A US3796137 A US 3796137A
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United States
Prior art keywords
cylinder
piston
carrier
rotary
drive member
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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US00224134A
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English (en)
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J Thoma
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Individual
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Individual
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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
    • 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
    • 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
    • F01B3/109—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block by changing the inclination of the axis of the cylinder barrel relative to the swash plate

Definitions

  • a hydraulic pump or motor of the tilting head or tilted head type including a number of separate piston and cylinder units each capable of independent pivotal movement and each including a ball and socket joint at opposite ends and a bearing slipper at one end abutting against a stationary thrust surface.
  • the fluid is admitted and discharged from the cylinders either through the bearing slipper or through a door in the piston.
  • the rotary axis of the cylinder carrier is inclined at a fixed angle or angularly adjustable in relation to the ro tary axis of the drive member so that as the two parts rotate together the individual pistons reciprocate in the cylinders, the volumetric capacity of the machine being determined by the relative angular inclination of the two main rotary axes.
  • Various methods have been adopted hitherto for causing the roatry drive member and the rotary cylinder carrier to rotate in unison.
  • the pistons themselves are used to transmit the driving torque between the two parts, and it has also been proposed to provide a constant velocity universal joint, or a star-shaped synchronising device, for coupling the two parts together.
  • the invention consists in an axial piston rotary hydraulic pump or motor, of the tilted or tilting head type, comprising a rotary drive member and a rotary cylinder carrier whose rotary axes are inclined or inclinable, a plurality of separate piston and cylinder assemblies, supported individually by the cylinder carrier so as to be capable of individual pivotal movernents, and each connected to the rotary drive member, each piston and cylinder assembly including a pivotal joint at opposite ends and a bearing slipper connected to one ofthe pivotal joints and arranged to bear against a relatively stationary abutment member.
  • each abutment member is located at the end of the cylinder carrier remote from the rotary drive member.
  • the carrier has longitudinally extending guide means for each cylinder.
  • This may be formed by a pair of spaced radial flanges on the carrier.
  • Each flange may be formed with a bore, aligned with a corresponding bore in the other flange, and these bores may be arranged to engage the cylinder directly or indirectly.
  • one of the bores at the end remote from the drive member may be arranged to locate the respective bearing slipper, which in turn locates the adjacent end of the corresponding cylinder.
  • one of the flanges, adjacent the drive member may be replaced by a star-shaped member having projecting fingers designed to lie partly between the cylinders.
  • the drivemember has locating formations to locate the ends of the pistons, the pitch circle diameter of such formations being greater than the pitch circle diameter of the opposite ends of cylinders in the cylinder carrier.
  • each bearing slipper has a flow passage communicating with the interior of the respective cylinder, and with a timing port in the cylinder carrier, the timing port communicating respectively with fluid admission and delivery ports in the abutment member as the carrier rotates.
  • the flow ports in the abutment member will preferably be located closer to the rotary axis than the bearing slippers.
  • each piston is preferably connected via one of the pivotal joints to an individual thrust member carried by the rotary drive member, and provided with a bearing element engaging an axial abutment surface opposing the thrust of the. pistons.
  • Each such thrust member may be itself pivotally connected to the respective bearing element.
  • each piston has a flow passage communicating respectively with the interior of the associated cylinder and with a timing portin the rotary drive member, the timing ports communicating successively with fluid admission and delivery ports in a non-rotary distributor member.
  • bearing slippers are preferably lubricated by fluid flow passages in the respective slippers, each communicating via one of the pivotal joints with the internal volumes of the respective cylinders.
  • FIG. 1 is a somewhat diagrammatic sectional side elevation through the main operating components of an axial piston tilting head hydraulic pump or motor according to the invention
  • FIG. 2 is a similar sectional side elevation through another example of the invention.
  • FIG. 3 is a cross-section on a plane corresponding to the line III-III in FIG. 1, showing a modification of the first illustrated example.
  • the machine illustrated is a hydraulic pump, though it will be understood that the same machine can be operated as a motor.
  • the machine includes a rotary drive shaft 10 mounted in a thurst bearing 11 from a non-rotary fixed casing member 12.
  • the drive shaft is rigidly secured to a drive flange 13 supported by a surrounding roller bearing 14.
  • a rotary cylinder carrier indicated generally at 15 has a stub shaft or spigot 16 fitting in a part-spherical member 17 received in a corresponding part-spherical recess at the centre of the drive flange 13.
  • the member 17 is located by a fixing plate 18.
  • the carrier 15 comprises a pair of radial flanges 20, 21 rigidly connected to or formed integral with a central spool 22.
  • the flange 20 remote from the drive shaft has a series of angularly spaced cylindrical bores each receiving the cylindrical stem of a bearing slipper 26. These slippers engage the surface 27 of an abutment member 28 formed with a central bearing aperture 29 to receive and locate a projecting stub or spindle 30 on the adjacent end of the rotary carrier 15.
  • the abutment member 28 may be fixed with its abutment surface 27 inclined to the rotary axis 32 of the drive shaft, but in this example of an adjustable tilting head pump the abutment member 28 is rigidly connected to a pair of arms 9 mounted on trunnions indicated diagrammatically at 33, capable of rocking about a transverse tilting axis which intersects the centre 34 of the spherical joint 17.
  • the tilting movements of the arms 9 carrying the abutment member 28 can be controlled by a conventional tilting mechanism, and cause corresponding bodily tilting movements of the whole rotary cylinder carrier 15 about the tilting axis 34, and so vary the volumetric capacity of the machine in well known manner.
  • Each bearing slipper 26 is formed with a partspherical socket 37 receiving a part-spherical ball head 38 at the adjacent end of the respective cylinder 40.
  • This cylinder extends through a corresponding cylindrical aperture 41 in the other radial flange 21, the external surface of the cylinder being formed with a conical tapered surface 42, reducing in diameter towards the end of the cylinder and thus providing a small annular clearance around the cylinder where it passes through the guide aperture 41. This allows small bodily tilting movement of the cylinder about the centre of the corresponding ball and socket joint 37, 38.
  • each cylinder is mounted a sliding piston 45 whose end porjects from the cylinder and is formed with a partspherical ball head 46 seating in a corresponding partspherical socket 47 formed in the rotary drive flange 13, the head being located in the socket by the fixing plate 'l8.
  • the pitch circle diameter of the sockets 47 is slightly greater than the pitch circle diameter of the sockets 37.
  • the piston 45 has a central flow passage 50 of substantial diameter and this communicates via the ball 46 with a flow passage 51 extending through the drive flange 13 and having a port at its opposite end which acts as a timing port to communicate successively with one of two kidneyshaped arcuate fluid delivery and admission ports in the fixed casing member 12.
  • one of these flow ports is illustrated at 52 communicating via a passage 53 with an external hydraulic circuit.
  • the face of the bearing slipper 26 which engages the abutment surface 27 is lubricated by hydraulic fluid supplied from the interior volume 54 of the cylinder.
  • the end of the cylinder including the ball head 38 is formed with a small-bore drilling 55 which communicates with a further drilling 56 in the slipper, this in turn communicating with a shallow depression 57 formed in the end face of the slipper.
  • the flow of hydraulic fluid to the face of the slipper for lubricating purposes can be controlled or metered by providing throttling orifices in one or more of the lubricating supply passages.
  • the throttling re striction may be provided at the co-operating spherical surfaces of the slipper 26 and the cylinder ball head 38.
  • each cylinder 40 has a comparatively large central flow passage 55 communicating with a similarly enlarged drilling 56' in the slipper.
  • This drilling communicates with a transverse bore 60, and in turn with a flow passage 61 formed within the radial flange 20' of the cylinder carrier.
  • This passage 61 opens into the axial end face of the flange, where it forms a timing port communicating with one of two kidney-shaped arcuate supply and delivery ports 62 in the non-rotary abutment member 28. Each of these ports 62 communicates with a fluid flow passage 63. In the case of a fixed capacity tilted head pump this passage 63 will communicate directly with an external hydraulic fluid circuit, but in the case of a tilting head pump as illustrated where the whole cylinder carrier 15 with the abutment member 28' can rotate about the tilting axis, the passages 63 communicate via passages within the arms 9 with flow passages in hollow trunnions 33.
  • the drive flange is formed with a number of angularly spaced through drillings in each of which is accommodated a generally cylindrical thrust element 71 which is a sliding fit in the passage 70.
  • This thrust element 71 has a pair of part-spherical recesses 72, 73 at opposite ends, one of which co-operates with the ball head 46' on the end of the piston 45', while the other receives a ball head 74 on a further bearing slipper 75.
  • the bearing surface of this slipper engages against a thrust surface 76 formed on the fixed casing member 12 surrounding the drive shaft 10'.
  • the bearing surface of each slipper is lubricated by hydraulic fluid from the internal volume 54 of the respective cylinder by small-bore passages 77, 78, 79, in the piston itself, in the thrust element 71, and in the bearing slipper 75.
  • the supply of oil for lubricating purposes may be throttled or metered by an appropriately shaped slot or groove 80 formed in the spherical ball head of the slipper.
  • the slipper 26 may be formed in two parts with an intervening ball and socket joint, one part being accurately guided as a sliding fit within the cylindrical aperture 25' of the cylinder carrier, while the actual bearing head or pad of the slipper is permitted to tilt or pivot to accommodate small angular misalignments.
  • a radial or pintle type timing valve and distributor may be used if preferred.
  • the spherical joints between the various components since only very small relative angular movements are involved, may be replaced by a layer of a suitable elastomeric material between the two components, having sufficient elasticity and resilience to transmit the necessary axial thrust and to permit the small angular movements due to misalignment.
  • the ball head 38 or 38' of the cylinder 40 or 40 is located in a socket in the respective bearing slipper 26 or 26', and the slipper itself is located in the cylindrical socket in the rotary cylinder carrier.
  • the end of the cylinder may be directly located in the cylinder carrier, for which purpose the socket or recess in the carrier will be formed with a part-spherical surface to accommodate the small tilting movement of the cylinder.
  • the third example of the invention illustrated in FIG. 3 is basically similar in construction to that illustrated in FIG. 1, and only points of difference will be described, all remaining features being identical and indicated by the same reference numerals as in FIG. 1, with a double suffix.
  • the apertures 41 in the flange 21 of the carrier are in effect enlarged in diameter until each aperture opens into the adjacent apertures, and the surrounding hoop or ring is eliminated.
  • the actual construction illustrated in FIG. 3 comprises a star-shaped element 80, replacing the flange 21 of FIG. 1, and formed with seven limbs or points 81 projecting outwards partly between the cylinders 40", and intervening concave arcuate surfaces 82 concentric with the individual cylinders. This construction allows somewhat greater tilting movements of the individual cylinders,
  • the other flange of the cylinder carrier is formed with separate non-overlapping bores, similar to the bores 25 of FIG. 1.
  • An axial piston rotary hydraulic machine of the tilted or tilting-head type comprising a rotary drive member, a rotary cylinder carrier, means for supporting said cylinder carrier with its rotary axis inclined or inclinable relative to the axis of said drive member, a plurality of separate piston and cylinder assemblies, each assembly being supported individually by the cylinder carrier so as to be capable of individual pivotal movements relative thereto, and each connected at one end to said rotary drive member, each piston and cylinder assembly including pivotal joints at opposite ends thereof, a relatively stationary abutment member adjacent one end of said cylinder carrier; and a bearing slipper connected to one of said pivotal joints of each of said piston and cylinder assemblies and arranged to bear against said abutment member, each of said bearing slippers having a flow passage communicating with the interior of the respective cylinder, and with a timing port in the cylinder carrier, the timing port communicating respectively with fluid admission and delivery ports in said abutment member, as the carrier rotates.
  • a hydraulic machine in which said abutment member is located at one end of said cylinder carrier, and said rotary drive member is located at the other end of said carrier.
  • a hydraulic machine in which the external surface of each cylinder, at the end thereof adjacent the drive member, is conically tapered to a smaller diameter at its end.
  • a hydraulic machine in which said drive member has locating formations to locate the ends of said pistons, the pitch circle diameter of such locating formations being greater than the pitch circle diameter of the opposite ends of the cylinders in the cylinder carrier.
  • each piston is pivotally connected via one of said pivotal joints to an individual thrust member carried by said rotary drive member, each thrust member being provided with a bearing element engaging an axial abutment surface opposing the thrust of the pistons.
  • each of said thrust members is pivotally connected to the respective bearing element.
  • bearing slippers are lubricated by fluid flow passages in the respective slippers, each communicating via one of said pivotal joints with th internal volumes of the respective cylinders.
  • An axial piston rotary hydraulic machine of the tilted or tilting head type comprising a rotary drive member, a rotary cylinder carrier, means for supporting said cylinder carrier with its rotary axis inclined or inclinable relative to the 'axis of said drive member, a plurality of separate piston and cylinder assemblies, each assembly being supported individually by the cylinder carrier so as to be capable of individual pivotal movements relative thereto, and each connected at one end to said rotary drive member, each piston and cylinder assembly including pivotal joints at opposite ends thereof, a relatively stationary abutment member adjacent one end of said cylinder carrier, and a bearing slipper connected to one of said pivotal joints of each of said piston and cylinder assemblies and arranged to bear against said abutment member, each piston having a flow passage communicating respectively with the interior of the associated cylinder and with a timing port in the rotary drive member, the timing ports communicating successively with fluid admission and delivery ports in a non-rotary distributor member.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
US00224134A 1971-02-11 1972-02-07 Rotary hydraulic machines Expired - Lifetime US3796137A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH232071A CH534807A (de) 1971-02-11 1971-02-11 Axialkolbenmaschine mit einzelnen Zylindern

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US3796137A true US3796137A (en) 1974-03-12

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US00224134A Expired - Lifetime US3796137A (en) 1971-02-11 1972-02-07 Rotary hydraulic machines

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US (1) US3796137A (de)
CH (1) CH534807A (de)
DE (1) DE2205469A1 (de)
GB (1) GB1351887A (de)
IT (1) IT951026B (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3885459A (en) * 1970-02-20 1975-05-27 New Invent Sa Telescopic piston-cylinder assembly for hydraulic machines and machinery components
US4075933A (en) * 1976-06-04 1978-02-28 Gresen Manufacturing Company Hydraulic pump or motor
DE2921902A1 (de) * 1978-06-02 1979-12-13 Centre Techn Ind Mecanique Mehrzylindrige, hydraulische pumpe bzw. motor mit pumpenstiefel und mit durch dessen neigung veraenderbarem volumen
RU2300014C2 (ru) * 2002-08-26 2007-05-27 Сергей Иванович Тюменцев Аксиальная гидромашина
CN108150398A (zh) * 2016-12-05 2018-06-12 江苏汉力士液压制造有限公司 球窝可换式斜盘

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2119867B (en) * 1982-05-07 1986-02-05 Raymond Albert Buckell Multi-cylinder device

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2146133A (en) * 1936-06-01 1939-02-07 Waterbury Tool Co Power transmission
US2157692A (en) * 1936-04-29 1939-05-09 Waterbury Tool Co Power transmission
DE1161762B (de) * 1961-11-16 1964-01-23 Hymate Ges Fuer Hydraulische A Axialkolbenpumpe
US3123014A (en) * 1964-03-03 Gregor
FR1360981A (fr) * 1963-06-19 1964-05-15 Licentia Gmbh Pompe à piston axial réglable en continu
US3149577A (en) * 1959-08-24 1964-09-22 Licentia Gmbh Axial piston machine
US3190231A (en) * 1962-04-06 1965-06-22 Dowty Hydraulic Units Ltd Hydraulic apparatus
US3240159A (en) * 1962-07-20 1966-03-15 Dowty Hydraulic Units Ltd Hydraulic apparatus
DE1453433A1 (de) * 1962-06-20 1969-03-27 Breinlich Dr Richard Tangentialbalancierungsfelder an Kolben in Rotations-Radialkolbenmaschinen mit Fluessigkeits- oder Gasbetrieb
US3722372A (en) * 1970-04-03 1973-03-27 Gen Electric Hydraulic axial piston machine of the bent-axis type

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3123014A (en) * 1964-03-03 Gregor
US2157692A (en) * 1936-04-29 1939-05-09 Waterbury Tool Co Power transmission
US2146133A (en) * 1936-06-01 1939-02-07 Waterbury Tool Co Power transmission
US3149577A (en) * 1959-08-24 1964-09-22 Licentia Gmbh Axial piston machine
DE1161762B (de) * 1961-11-16 1964-01-23 Hymate Ges Fuer Hydraulische A Axialkolbenpumpe
US3190231A (en) * 1962-04-06 1965-06-22 Dowty Hydraulic Units Ltd Hydraulic apparatus
DE1453433A1 (de) * 1962-06-20 1969-03-27 Breinlich Dr Richard Tangentialbalancierungsfelder an Kolben in Rotations-Radialkolbenmaschinen mit Fluessigkeits- oder Gasbetrieb
US3240159A (en) * 1962-07-20 1966-03-15 Dowty Hydraulic Units Ltd Hydraulic apparatus
FR1360981A (fr) * 1963-06-19 1964-05-15 Licentia Gmbh Pompe à piston axial réglable en continu
US3722372A (en) * 1970-04-03 1973-03-27 Gen Electric Hydraulic axial piston machine of the bent-axis type

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3885459A (en) * 1970-02-20 1975-05-27 New Invent Sa Telescopic piston-cylinder assembly for hydraulic machines and machinery components
US4075933A (en) * 1976-06-04 1978-02-28 Gresen Manufacturing Company Hydraulic pump or motor
DE2921902A1 (de) * 1978-06-02 1979-12-13 Centre Techn Ind Mecanique Mehrzylindrige, hydraulische pumpe bzw. motor mit pumpenstiefel und mit durch dessen neigung veraenderbarem volumen
US4253381A (en) * 1978-06-02 1981-03-03 Centre Technique Des Industries Mechaniques Hydraulic machine of the multicylinder drum type
RU2300014C2 (ru) * 2002-08-26 2007-05-27 Сергей Иванович Тюменцев Аксиальная гидромашина
CN108150398A (zh) * 2016-12-05 2018-06-12 江苏汉力士液压制造有限公司 球窝可换式斜盘

Also Published As

Publication number Publication date
CH534807A (de) 1973-03-15
GB1351887A (en) 1974-05-01
DE2205469A1 (de) 1972-11-30
IT951026B (it) 1973-06-30

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