US3802321A - Rotor balancing arrangement for axial piston machines - Google Patents

Rotor balancing arrangement for axial piston machines Download PDF

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Publication number
US3802321A
US3802321A US00269266A US26926672A US3802321A US 3802321 A US3802321 A US 3802321A US 00269266 A US00269266 A US 00269266A US 26926672 A US26926672 A US 26926672A US 3802321 A US3802321 A US 3802321A
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Prior art keywords
pressure
control face
cylinder block
pressure chamber
ring
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Expired - Lifetime
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US00269266A
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English (en)
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P Bosch
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • F01B3/0041—Arrangements for pressing the cylinder barrel against the valve plate, e.g. fluid pressure
    • 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
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/0064—Machine housing
    • 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

Definitions

  • the cylinder block of an axial piston machine includes a rotary control face pressed against a stationary control face having inlet and outlet ports.
  • a peripheral Foreign Appllcatlon y Data annular shoulder of the cylinder block cooperates with July 6, 1971 1 Germany 2134026 an annular shoulder on a pressure ring surrounding the cylinder block so that a pressure chamber is [52] US. Cl. 91/485 formed, communicating through a channel including a [51] Int. Cl. F01b 13/04 check valve, with an annular groove in the stationary [58] Field of Search 91 /485, 486, 487, 489 control face connected by a throttle duct with a low pressure area.
  • the present invention relates to axial piston machines, pumps or motors, which are provided with pressure chambers for pressing the cylinder block against a stationary control face having inlet and outlet ports.
  • annular shoulder is provided on the peripheral surface of the cylinder block, and an annular pressure ring, which surrounds the cylinder block is provided with a corresponding shoulder, forming a pressure chamber.
  • the pressure ring is mounted in the housing for universal tilting movement which has the advantage that the pressure ring can align itself in axial direction with the cylinder block, and transmits no tilting forces to the cylinder block. Consequently, the entire rotary end face of the cylinder block fully abuts the entire surface of the stationary control face of the housing so that leakage losses from a gap between the slidingly engaged control faces are avoided.
  • FIG. 1 is an axial sectional view illustrating an axial piston machine provided with the apparatus of the invention
  • FIG. 2a is a front view
  • FIG. 2b is a side view illustrating a universally tiltable supporting ring for the embodiment of FIG. 1;
  • FIG. 3 is a side view, partially in axial section, illustrating a modification of the embodiment of FIG. 1;
  • FIG. 4 is an axial sectional view taken on line IV-IV in FIG. 3, and particularly illustrating the construction of a stationary control face on the housing;
  • FIG. 5 is a cross-sectional view taken on line VV in FIG. 3;
  • FIG. 6 is a fragmentary sectional view taken on line VI-VI in FIG. 5;
  • FIG. 7a is a front view
  • FIG. 7b is a side view illustrating a universally tiltable supporting ring for the embodiment of FIGS. 3 to 6.
  • an axial piston machine has a housing 1 closed by a cover 2.
  • a rotor shaft 3 is mounted in housing 1 in a ball bearing 4, and in the cover 2 in a roller bearing 5, and connected by a splined shaft portion 6 with a cylinder block 7 for rotation.
  • Cylinder bores 8 are provided in cylinder block 7 concentric and parallel to the axis of shaft 3, and contain pistons 12 provided with slide shoes 9 slidingly abutting a sliding surface 10 of a wobble plate 11.
  • a holding ring 14 secured in a cover ring 13 abuts on the slide shoes and prevents a separation of the slide shoes from the slide surface 10.
  • the rotor shaft 3 passes through the cylinder block 7 permitting by the splines 6 a limited axial movement of cylinder block 7.
  • the cylinder bores 8 have frustoconical end portions 21' forming cylinder ports 21 of reduced cross-section which cooperate with part circular inlet and outlet ports 22, 23 in the stationary control face 20 which are supplied with pressure fluid by the inlet and outlet means 24, 25.
  • the arrangement is well known, and corresponds substantially to elements 60, 61, 54, 55 shown in FIG. 4 for another embodiment of the invention.
  • the stationary control face 20 is further provided with an annular groove 26 surrounding the control ports 22, 23, and connected by a conduit 28 including a throttle duct 27 wiht a discharge channel 30 which opens into a low pressure area, such as a reservoir for leakage oil.
  • a pressure ring 32 surrounds the outer peripheral surface of cylinder block 7, and has an axially extending recess into which a pin 31 mounted on the housing 1 projects so that the pressure ring 32 is movable in axial direction, but prevented from rotation.
  • An annular shoulder is formed about the periphery of cylinder block 7 and includes the cylindrical peripheral surface 7' of the cylinder block, and an annular pressure surface 7" facing toward the wobble plate 1 1.
  • the annular shoulders 7 and 32', the cylindrical face 32", and the peripheral surface 7 together form a pressure chamber 33 which is so disposed that pressure fluid in the annular pressure chamber 33 urges the cylinder block 7 to move to the left as viewed in FIG. 1.
  • FIGS. 2a and 2b show the construction of the supporting ring 37 in detail.
  • two diametrical projections 40, 40, and on the other lateral annular surface 41 two diametrically disposed projections 42, 42 are made.
  • the projections have a part circular outline and are cylindrical in axial direction.
  • the line of symmetry between projections 42, 42, and the line of symmetry between the projections 40 and 40 intersect at right angles in the axis of cylinder block 7 and shaft 3.
  • the pressure in the high pressure conduit 25 or 24 drops, the pressure also drops in the cylinder bores 8 which communicate with the inlet and outlet ports, and the forces acting on the reduced portions 21 of the cylinder bores 8, and pressing the cylinder block 7 against the control face 20, are also reduced, while the forces acting in the gap between stationary control face 20 and rotary control face 7a to displace rotor 7, to increase the width of the gap, are reduced due to the throttle effect at a smaller rate.
  • the annular pressure surface 7" of cylinder block 7, on which the pressure in pressure chamber 33 acts is so dimensioned that the pressure forces are sufficient to compensate the forces tending to lift the cylinder block off the stationary control face.
  • the check valve 34 closes immediately, and the pressure in the annular pressure chamber 33 rises due to the compression of the pressure fluid caused by the tilting movement, so that a further tilting is reliably prevented.
  • the annular pressure chamber 33 has the effect that the forces transmitted from the pressure ring 32 to the supporting ring 37 are uniformly distributed about the circumference of the supporting ring, while the point at which the forces act coincides with the axis of rotation of the cylinder block 7. Due to the arrangement of the abutments 40, 40' and 42, 42', permitting tilting in two perpendicular directions, supporting ring 37 provides a Cardan-like support for the pressure ring 32 which is free to align itself in axial direction with the cylinder block 7 so that no tilting force is exerted on the cylinder block 7 due to the force pressing the cylinder block against stationary control face 20, since in this type of support by supporting ring 37, the pressure force of the annular face 32, and the reaction force of the supporting ring 37, which acts on the pressure ring 32, have coinciding resultant force lines.
  • FIG. 3 illustrates an embodiment of the invention which is suitable as a pump in which fluid always flows in the same direction. Corresponding parts are indicated by the same reference numerals in FIG. 3 as in FIG. 1.
  • the pump shown in FIG. 3 has a housing 1 closed by a cover having a stationary control face 51 confronting a rotary control face 67a on the cylinder block 67.
  • the stationary control face 51 is best shown in FIG. 4, from which it is apparent that part-circular inlet and outlet ports 54 and 55 are provided with fluid through conduits and 61, conduit 60 being assumed to be the high pressure conduit.
  • Concentric to the inlet and outlet control ports 54, 55, which are separated by face portions 52, 53, two part circular grooves 58, 59 sepa rated by face portions 56 and 57 are provided.
  • a line of symmetry between face portions 52, 53 coincides with the line of symmetry for groove portions 58 and 59.
  • the groove portion 58 communicate with a conduit 63 which includes a throttling duct 62, shown in FIGS. 3 and 4.
  • Conduit 64 is connected with a low pressure area.
  • Another throttle duct 65 connects the center of groove part 59 with a conduit 66 connected with conduit 64 and a low pressure area.
  • the cylinder block 67 which has an inner stepped bore 15 through which the rotor shaft 3 passes, is biassed by spring 17 abutting a disc 18 secured by a ring 19 inserted into an annular recess in bore 15 so that the rotary control face 67a is pressed against the stationary control face 51.
  • the cylinder bores with pistons 12 are arranged along a circle concentric with the axis of cylinder block 67 and have reduced portions 68 ending in rotor ports which communicate with the inlet and outlet ports 54, 55.
  • the cylinder block 67 is surrounded by a pressure ring 69 which forms with a shoulder 77 on cylinder block 67, two semi-circular pressure chambers 72, 73, separated by sealing pistons 70, 71 as best seen in FIGS. 5 and 6.
  • the pistons 70, 71 are slidingly mounted in stepped bores 74, 75 provided in the pressure ring 69, and have peripheral surfaces in sealing engagement with the cylindrical surfaces of the cylinder block 67 and pressure ring 85.
  • the sealing pistons 70, 71 are biassed by springs 76 into sealing abutment with the shoulder 77 of the cylinder block 67.
  • a line connecting the axes of the sealing pistons 70, 71 coincides with the line of symmetry through face portions 52, 53, 56, 57
  • Two diametrically opposite channel means 78 and 79 are provided in the cylinder block 67 which connect the rotary control face 7a with the pressure chamber portions 72 and 73, opening on the annular shoulder 77 on the outer periphery of cylinder block 67.
  • Channels 78, 79 connect the groove parts 58, 59 with the pressure chamber parts 72, 73.
  • the width of the face portions between the ports 58, 59 in the stationary control face 51 is dimensioned so that the ports of the channels 78, 79, which cooperate with grooved parts 58, 59 are closed over the same. angle as the ports in annular shoulder 77 are closed by the sealing pistons 70, 71.
  • a check valve 80, 81 is provided whose ball 83, 83' abuts a seat formed by a threaded bushing 84, 84' due to the action of a spring 82, 82, respectively.
  • the pressure ring 69 abuts a supporting ring 85 which abuts on its other side on a shoulder 38 of housing 1
  • Pressure ring 69 and supporting ring 85 have axial grooves into which stationary pins 31, 36 project to block rotational movement of pressure ring 69 and supporting ring 85.
  • the construction of the supporting ring 85 is best seen in FIGS. 7a and 7b.
  • Supporting ring 86 has on one annular face 86, which confronts the housing shoulder 38, two projections 87, 88 which are diametrically disposed on an axial plane, and has on the other side 89 two corresponding projections 90, and 91 which are respectively spaced different angular distances from projections 87 and 88, as best seen in FIG. 7a.
  • Each projection has a part circular outline and forms a corresponding cylinder.
  • the cylinder block 87 is pressed by spring 17 and by the fluid pressure acting on the frustoconical portions 68 of the cylinder bores 8, against the stationary control face 51.
  • pressure fluid flows out.
  • Pressure develops between the abutting control faces, tending to separate the rotary control face 67a from the stationary control face 51.
  • a part of the leaking pressure fluid enters the groove portion 58 which extends about the high pressure port 54 from where the fluid can flow through the throttling duct 62 conduit 63 and conduit 64 to a low pressure area.
  • a comparatively smaller amount of pressure fluid flows into the other groove part 59, and flows through throttling conduit 65, and conduit 66 and conduit 64 to the low pressure area upstream of the throttle duct 62, 65, pressure develops in the groove parts 58, 59 which produce a force acting on the rotary control face 67a to move the same way from the stationary control face 51.
  • the pressure in the groove part 58, communicating with the high pressure port 54, is greater than the pressure in groove part 59 in region of the low pressure port 55, and consequently, a greater force acts in the region of groove part 58 than in the region of groove part 59, to urge the cylinder block 67 away from the stationary control face 51 so that the center of the resultant of the forces is displaced relative to the rotor axis.
  • lf cylinder block 67 assumes a position in which the channels 78, 79 sweep the groove parts 58, 59, and if the pressure in the groove parts 58, 59 is sufficiently great to overcome the force of the spring of the check valves 80, 81, pressure fluid enters the two pressure chamber parts 72 and 73.
  • one of the channels for example channel 78 which connects the groove parts 58 with the pressure chamber part 72, is substantially at the same time closed by face portion on the stationary control face 57a, as a sealing piston 70, 71 closes a pressure chamber part and connects, when the channel ports are open again, the groove part 89 with the pressure chamber part 73.
  • the second channel 79 which until now had connected groove part 59 and pressure chamber part 73, connects the groove part 58 with the pressure chamber part 72. Due to the provision of two diametrically disposed channels, the communication between a pressure chamber part and a groove part is only interrupted as long as the channel ports are closed either by a control face portion of the stationary control face 51, or by a sealing piston 72, 71.
  • the center of the forces exerted by pressure ring 69 and pressure chamber parts 72, 73 coincides substantially with the reaction forces acting on the same point.
  • the universally movable supporting ring permits an alignment of the pressure ring 69 in axial direction of the cylinder block 67 so that no tilting forces can act on the cylinder block 67 caused by the forces pressing the cylinder block 67 toward the stationary control face 51.
  • one of the channels for example channel 78, may be omitted, together with the throttling duct 65 in conduit 77. In such an arrangement the forces which bias the cylinder block 67 against the stationary control face 51, are reduced.
  • Rotor balancing arrangement for axial piston machines comprising housing means having a stationary control face and a wobble surface confronting each other; rotor means mounted in said housing means for rotation, and including a rotary cylinder block having a rotary control face slidingly engaging said stationary control face, pistons mounted in cylinder bores of said cylinder block and having free ends sliding on said wobble surface, the pressure in said cylinder bores urging said rotary control face against said stationary control face, said cylinder block having a peripheral annular should facing toward said wobble surface; a pressure ring surrounding said cylinder block and mounted thereon for axial movement, said pressure ring having an annular shoulder forming with said peripheral annular shoulder at least one pressure chamber; channel means connecting said pressure chamber with the gap between said control faces so that an increase of the pressure in said gap causes an increase of the pressure in said pressure chamber whereby said rotary control surface is urged against said stationary control face; and a tiltable supporting ring between said pressure ring and an annular shoulder of said housing means for axially supporting said pressure ring
  • Rotor balancing arrangement for axial piston machines comprising housing means having a stationary control face and a wobble surface confronting each other, said stationary control face having inlet and outlet ports for fluid at different pressures, and a circular groove divided into two groove parts and located radially outward of said inlet and outlet ports; rotor means mounted in said housing means for rotation, and including a rotary cylinder block having a rotary control face slidingly engaging said stationary control face, pistons mounted in cylinder bores of said cylinder block and having free ends sliding on said wobble surface, the pressure in said cylinder bores urging said rotary control face against said stationary control face, said cylinder block having a peripheral annular shoulder facing toward said wobble surface; a pressure ring surrounding said cylinder block and mounted thereon for axial movement, said pressure ring having an annular shoulder forming with said peripheral annular shoulder at least one pressure chamber; means for dividing said pressure chamber into two pressure chamber parts; channel means connecting said pressure chamber with a gap between said control faces so that an increase of the pressure in said gap causes
  • Rotor balancing arrangement as claimed in claim 2 wherein said housing means has two throttle conduits connecting said groove parts with a low pressure area, respectively.
  • each of said channels includes adjustable check valve means opening at a predetermined pressure at the respective groove part to permit high pressure fluid and low pressure fluid from the gap between said control faces to enter said pressure chamber parts.
  • Rotor balancing arrangement as claimed in claim 3 wherein said tiltable supporting ring has on either side a pair of projections abutting said pressure ring and said shoulder of said housing means, respectively, wherein lines through said pairs of projections, respectively, intersect at right angles at a point spaced from the axis of said rotor means.
  • Rotor balancing arrangement for axial piston machines comprising housing means having a stationary control face and a wobble surface confronting each other; rotor means mounted in said housing means for rotation, and including a rotary cylinder block having a rotary control face slidingly engaging said stationary control face, pistons mounted in cylinder bores of said cylinder block and having free ends sliding on said wobble surface, the pressure in said cylinder bores urging said rotary control face against said stationary control face, said cylinder block having a peripheral annular shoulder facing toward said wobble surface; a pressure ring surrounding said cylinder block and mounted thereon for axial movement, said pressure ring having an annular shoulder forming with said peripheral annular shoulder at least one pressure chamber; rigid channel means connecting said pressure chamber with the gap between said control faces so that an increase of the pressure in said 'gap causes an increase of the pressure in said pressure chamber whereby said rotary control surface is urged against said stationary control face; and a tiltable supporting ring between said pressure ring and an annular shoulder of said housing means for axially
  • Rotor balancing arrangement as claimed in claim 1 wherein said projections of said pairs are spaced 180, and wherein said lines intersect at right angles at the axis of said rotor means; and wherein said pressure chamber is annular.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)
US00269266A 1971-07-08 1972-07-05 Rotor balancing arrangement for axial piston machines Expired - Lifetime US3802321A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2134026A DE2134026A1 (de) 1971-07-08 1971-07-08 Axialkolbenmaschine

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US3802321A true US3802321A (en) 1974-04-09

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US00269266A Expired - Lifetime US3802321A (en) 1971-07-08 1972-07-05 Rotor balancing arrangement for axial piston machines

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US (1) US3802321A (cg-RX-API-DMAC10.html)
DE (1) DE2134026A1 (cg-RX-API-DMAC10.html)
FR (1) FR2145265A5 (cg-RX-API-DMAC10.html)
GB (1) GB1350712A (cg-RX-API-DMAC10.html)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3933082A (en) * 1972-08-16 1976-01-20 Hans Molly Axial piston type machine
WO1981000597A1 (en) * 1979-08-27 1981-03-05 Caterpillar Tractor Co Radial piston fluid translating device with power conserving scavenging means
US4622885A (en) * 1984-01-31 1986-11-18 Sven Schriwer Hydrostatic piston pump or engine having diagonal piston axis
US6244160B1 (en) * 1997-02-18 2001-06-12 Brueninghaus Hydromatik Gmbh Axial piston machine with RMP-dependent pressure acting against the cylinder drum
US20170175721A1 (en) * 2015-12-17 2017-06-22 Nabtesco Corporation Fluid pressure pump and fluid pressure system
US11105203B2 (en) * 2018-01-29 2021-08-31 Carrier Corporation High efficiency centrifugal impeller with balancing weights
US11236736B2 (en) * 2019-09-27 2022-02-01 Honeywell International Inc. Axial piston pump with port plate having balance feed aperture relief feature
IT202300014367A1 (it) * 2023-07-10 2025-01-10 Walvoil Spa Pompa a pistoni

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4130225C1 (cg-RX-API-DMAC10.html) * 1991-09-11 1992-11-26 Brueninghaus Hydraulik Gmbh, 7240 Horb, De

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB311938A (en) * 1928-05-15 1929-05-23 John Robson Improvements in or connected with hydraulic pumps, motors, hydraulic transmission gears and the like
US1817080A (en) * 1929-04-10 1931-08-04 George E Howard Transmission mechanism
GB897700A (en) * 1957-07-06 1962-05-30 Bosch Gmbh Robert Improvements in or relating to hydraulic pumps and motors
US3208395A (en) * 1963-08-30 1965-09-28 Budzich Tadeusz Cylinder barrel suspension for fluid pressure energy translating device
US3618471A (en) * 1969-08-21 1971-11-09 Caterpillar Tractor Co Hydrodynamic thrust bearing for axial piston-type pump or motor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB311938A (en) * 1928-05-15 1929-05-23 John Robson Improvements in or connected with hydraulic pumps, motors, hydraulic transmission gears and the like
US1817080A (en) * 1929-04-10 1931-08-04 George E Howard Transmission mechanism
GB897700A (en) * 1957-07-06 1962-05-30 Bosch Gmbh Robert Improvements in or relating to hydraulic pumps and motors
US3208395A (en) * 1963-08-30 1965-09-28 Budzich Tadeusz Cylinder barrel suspension for fluid pressure energy translating device
US3618471A (en) * 1969-08-21 1971-11-09 Caterpillar Tractor Co Hydrodynamic thrust bearing for axial piston-type pump or motor

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3933082A (en) * 1972-08-16 1976-01-20 Hans Molly Axial piston type machine
WO1981000597A1 (en) * 1979-08-27 1981-03-05 Caterpillar Tractor Co Radial piston fluid translating device with power conserving scavenging means
US4265165A (en) * 1979-08-27 1981-05-05 Caterpillar Tractor Co. Radial piston fluid translating device with power conserving scavenging means
US4622885A (en) * 1984-01-31 1986-11-18 Sven Schriwer Hydrostatic piston pump or engine having diagonal piston axis
US6244160B1 (en) * 1997-02-18 2001-06-12 Brueninghaus Hydromatik Gmbh Axial piston machine with RMP-dependent pressure acting against the cylinder drum
US20170175721A1 (en) * 2015-12-17 2017-06-22 Nabtesco Corporation Fluid pressure pump and fluid pressure system
US10443584B2 (en) * 2015-12-17 2019-10-15 Nabtesco Corporation Fluid pressure pump and fluid pressure system
US11105203B2 (en) * 2018-01-29 2021-08-31 Carrier Corporation High efficiency centrifugal impeller with balancing weights
US11236736B2 (en) * 2019-09-27 2022-02-01 Honeywell International Inc. Axial piston pump with port plate having balance feed aperture relief feature
IT202300014367A1 (it) * 2023-07-10 2025-01-10 Walvoil Spa Pompa a pistoni

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Publication number Publication date
FR2145265A5 (cg-RX-API-DMAC10.html) 1973-02-16
GB1350712A (en) 1974-04-24
DE2134026A1 (de) 1973-01-18

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