US3847057A - Precharging arrangement for a hydraulic displacement machine - Google Patents

Precharging arrangement for a hydraulic displacement machine Download PDF

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Publication number
US3847057A
US3847057A US00240388A US24038872A US3847057A US 3847057 A US3847057 A US 3847057A US 00240388 A US00240388 A US 00240388A US 24038872 A US24038872 A US 24038872A US 3847057 A US3847057 A US 3847057A
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United States
Prior art keywords
cylinder
ports
inner space
low pressure
high pressure
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Expired - Lifetime
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US00240388A
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English (en)
Inventor
G Ital
H Baurle
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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
    • 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
    • F04B1/2014—Details or component parts
    • F04B1/2035—Cylinder barrels
    • 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
    • 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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • 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
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • 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
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates

Definitions

  • ABSTRACT An axial piston pump or motor whose'rotary cylinder block has cylinder chambers and pistons therein, has an end face with cylinder ports cooperating with a stationary control face having high pressure and low pressure ports. A closed inner space in the housing is maintained by pressure limiting throttle means at an intermediate pressure when filled with leakage fluid.
  • Control means including ducts connect the closed inner space with a cylinder chamber when the respective cylinder port is located on a control face portion between the high pressure and low pressure ports to fill the respective cylinder chamber with fluid at said intermediate pressure, and disconnecting the closed inner space from the cylinder chambers when the cy1- inder ports communicate with the high pressure and low pressure ports in the control face.
  • the present invention relates to a rotary displacement pump which has a cylinder block arranged in a closed housing and having working chambers in which displacement members are guided for reciprocating movement caused by engagement of projecting end portions of the displacement members with an actuating means.
  • the machine may be an axial or radial piston pump or hydraulic motor, or a vane pump or motor.
  • German 08 1,453,452 disclosed an axial piston hydraulic machine in which the end face of the cylinder block is pressed, in addition to the force of a spring, by hydraulic force against a stationary control face in order to avoid a separation or relative tilting of the slidingly engaging recess.
  • pressure fluid leaking from the gap between the two faces is accumulated in the inner closed space of the housing, and discharged through a throttle.
  • the throttle produces a predetermined pressure in the inner 'space of the housing, which also acts on the cylinder block for increasing the pressure by which the end face of the cylinder block is pressed against the stationary control face which is provided with high pressure and low pressure ports.
  • Another object of the invention is to fill the cylinder chambers of the cylinder block with fluid at an intermediate pressure during the time when the cylinder ports communicate neither with the high pressure port nor the low pressure port in the stationary control face, and the respective cylinder chamber is neither filled with high pressure fluid nor with low pressure fluid.
  • Another object of the invention is to provide control means for disconnecting the closed inner space in the housing from the cylinder chambers while the cylinder chambers are filled with high pressure fluid, so that no discharge of high pressure fluid into the closed inner space is possible.
  • an embodiemnt of the invention comprises closed housing means having an inner control face formed with part-circular high pressure and low pressure ports; actuating camming means secured to the housing means; cylinder block means mounted in the housing means and having an end face slidingly cooperating with the control face, throttle means connecting the closed inner space with the outside of the housing when leakage fluid at a predetermined pressure fills the inner space; and control means for disconnecting the closed inner space from the working chambers of the cylinder block means when the cylinder ports in the block end face are located on the high pressure and low pressure ports in the control face, and also for connecting the closed inner space with the respective working chamber when the respective cylinder port is located between the high pressure and low pressure ports on the control face so that the respective working chamber is filled with fluid from said closed inner space having a predetermined pressure.
  • each cylinder bore communicates with a duct which communicates with the closed inner space of the housing, but is only opened when the respective displacement member or piston is located in'the proximity of the lower dead center position of the reciprocating piston.
  • the duct means which connect the cylinder bore with the closed inner space of the housing, and which is opened shortly before the piston arrives in the lower dead center position, additional pressure fluid from the closed inner space of the housing flows into the cylinder chamber and improves the degree of filling with fluid.
  • the noise of operation is reduced since pressure fluid enters an insufficiently filled cylinder chamber in the prior art construction, and causes cavitation: and fluid oscillations, which are avoided by the precharging of the-cylinder chambers in accordance with the invention with fluid at an intermediate pressure.
  • the arrangement of the invention is particularly suited for displacement pumps having a suction inlet.
  • the arrangement according to the invention can be advantageously used with adjustable and unadjustable axial piston pumps with rotary cylinder block and stationary swash plate, and also for axial piston pumps with stationary cylinder block and-rotary swash plate, but it is possible to apply the novel features of the invention to radial piston pumps of various types.
  • control duct means include a duct through the swash plate opening in the closed inner space. In another embodiment of.
  • control duct means are provided in the cylinder block, and are connected with the respective cylinder chambers only when the piston is in the end position in which the cylinder chamber has the greatest volume.
  • control duct is provided in the pistons, and communicates with the closed inner space in the housing only when the piston is in the end position in which the volume of the respective cylinder chamber is-largest.
  • FIG. 1 is an axial sectional view illustrating an axial piston pump in accordance with the invention
  • FIG. 2 is a fragmentary cross-sectional view taken on line II-II in FIG. 1;
  • FIG. 3a is a fragmentary axial sectional view illustrating a second embodiment of the invention.
  • FIG. 3b is a fragmentary cross-sectional view taken on line llIIlI in FIG. 3a;
  • FIG. 4a is a fragmentary axial sectional view illustrating a third embodiment of the invention.
  • FIG. 4b is a fragmentary cross-sectional view taken on line IVIV in FIG. 4a.
  • a housing 1 is closed at one end by a bottom plate 6 and at the other end by a cover 2 which having bearings 6a and 2a supporting a drive shaft which is connected by an annular set of teeth 7 with a corresponding engaging set of inner teeth in the inner cavity 4 of a cylinder block 3.
  • a coil spring 8 surrounds a thin portion of shaft 5, abutting at one end a shoulder of shaft 5 and at the other end a spring ring secured to the cylinder block 3. The force of spring 8 urges the end face 3a of cylinder block 3 against the stationary control face 9a of a control valve member 9 which is secured to bottom wall 6, and consequently stationary.
  • valve plate 9 and its stationary control surface 9a is formed with part-circular high pressure and low pressure ports 10 and 11 which communicate with bores 12 and 13 in housing bottom wall 6.
  • Cylinder block 3 has cylinder chambers or working chambers 14 arranged along a circle concentric with the axis of shaft 5, and having cylinder ports 14 cooperating with the high pressure and low pressure ports 10, ll.
  • Displacement members in the form of pistons 15 are mounted in the cylinder chambers 14 for axial movement, and are provided at the free outer end portions thereof, with slide shoes 16 which slidingly engage a circular annular surface portion of the surface 22 of swash plate 17 during rotation of the cylinder block 3 relative to the swash plate 17, which is secured to the housing cover 2.
  • the pistons 14 have axially extending stepped ducts I8 communicating with ducts 19 in the respective slide shoes 16, and ending in a recess 20 in the end face of the slide shoe 16 which slides on surface 22 of the swash plate 17.
  • Another duct 21 is formed in the swash plate 17 which has one end in the circular annular surface portion swept by the end face and recess 20 of the slide shoes, and which opens at the other end in the closed inner space 23 of the housing. Consequently, in one relative position between the rotary cylinder block 3 and the stationary swash plate or other actuating means 17, the stepped duct 18, the slide shoe duct 19, the recess 20, and the duct 21 connect. the respective cylinder chamber 14 with the closed inner space 23.
  • FIG. 2 shows that the part-circular high pressure and low pressure ports 10 and 11 have ends spaced from each other so that a cylinder port moving from the position 14 to the position 14" is disconnected from the pressure ports 10 and 11.
  • the ports 21' of duct 21 in the surface 22 is located in an axial plane which is equidistant from the ends of the pressure ports 10 and 11, and the diameter of the recesses 20' in the slide shoes 16 is selected so that the same do not cover the port 21' before separated from the pressure ports 10 and 11.
  • the stepped bore 26 houses a pressure limiting throttle valve 29 having a closure element 29" biassed by spring 29 against a frusto-conical seat 30 formed in bore 26 so that flow of pressure fluid from the closed inner space 23 to the passage 13 is closed.
  • the pressure required for opening the pressure limiting valve 29 is very low, for example four bar.
  • the recess 20 in the slide face of slide shoe 16 covers the port 21 of the duct 21 which opens in the surface 22 of the swash plate 17 so that the cylinder bore 14 is connected with the closed inner space 23 in the housing by the ducts 18, 19, 21.
  • pressure fluid enters the closed inner space 23 where a pressure develops whose maximum depends on the pressure limiting throttle valve 29.
  • the valve opens so that pressure fluid can be discharged through discharge passage 28.
  • a small overlapping of the suction operation with the pre-compression and/or the discharge with pre-compression may occur if a small reduction of the efficiency due to the abovedescribed discharge of pressure fluid is permissible.
  • the control duct means include no duct in the swash plate 17 or other actuating means.
  • Radial ducts 24 are provided for connecting each cylinder chamber 14 with the closed inner space 23, each duct 24 having an inner end communicating with the respective cylinder chamber 14, and an outer end communicating with the inner space 23. While the opening and closing of the control duct means is obtained -in the embodiment of FIGS. 1 and 2 by the relative movement between the slide shoes 16 and the stationary duct 21, a corresponding opening and closing of the control ducts 24 is effected by the reciprocating movement of piston 15'. It will be seen that in the end position of piston 15 shown in FIG.
  • the control duct 24 is open, so that the fluid can flow from the inner space 23 into the respective cylinder chamber 14.
  • the piston 15 moves out of the illustrated dead center position, it covers the inner end of the control duct 24 and separates the inner space 23 from the cylinder chamber 14. This is necessary during communication of the cylinder ports 14' with the high pressure and low pressure ports and 11, as shown in FIG. 3b, in order to prevent flow from the high pressure duct 10 into the closed inner space 23.
  • the respective cylinder chamber 14, and its ports 14' are located between the ends of the part-circular cylinder ports 10 and 11, so that cylinder port 14' is closed, and the cylinder chamber 14 can be filled through control duct 24 from the closed inner space 23.
  • pistons 15 uncover, shortly before arriving at the dead center position, the control duct 24, after disconnecting cylinder port 14 of cylinder bore 14 from the suction passage 11. Pressure fluid from the closed inner space 23 flows into the cylinder chamber 14 so' that its degree of filling is improved, while the fluid in the cylinder chamber is pre-compressed. After reversal of its stroke, the piston 15 closes the control duct 24 before a cylinder port 14' of the respective cylinder bore covers the high pressure port 10. In this manner, it is prevented that pressure fluid flows from the closed inner space 23 to the suction low pressure port 11, or from the high pressure port 10 into the inner closed space 23 in the housing.
  • a diametrical control duct 25 connects an axial duct portion 18 in each piston 15 with the closed inner space 23.
  • the control ducts 25 are located directed adjacent an edge of a wall of the cylinder block 3, as shown in FIG. 4a.
  • the control duct means 25, 18 connect the closed inner space 23 with the respective cylinder chamber 14.
  • the cylinder port 14' registers neither with the high pressure port 10 nor with the low pressure port 11, as shown in FIG. 4b, but is closed by the face portion between the ends of the pressure ports 10 and 11 so that no fluid can flow into and out of cylinder chamber 14 which is being filled through the control ducts 25 and 18.
  • pistons 15 perform reciprocating motions during which the radial control ducts 25 are uncovered by the cylinder block 3 when, as shown in FIG. 4b, the communication between the cylinder port 14' of cylinder chamber 14 with the suction low pressure port 11 is interrupted, and the piston 15 is shortly before the respective dead center position.
  • Pressure fluid flows now through the The embodiment of FIGS. 4a and 4b prevents the' flow of fluid through the control ducts out of the cylinder chambers, or the flow of fluid out of the high pressure port 10 into the inner space 23 of the housing.
  • Precharging arrangement for a hydraulic displace- I ment machine comprising closed housing means having an inner control face formed with part-circular high pressure and low pressure ports; actuating means secured to said housing means; cylinder block means mounted in said housing means and having a cylinder block end face slidingly cooperating with said control face, said cylinder block means including working chambers opening in cylinder ports on said end face so that said high pressure and low pressure ports communicate with said cylinder ports during relative'rotation 4 of said housing means and said cylinder block means,
  • said cylinder block means including displacement members in said working chambers having free end portions cooperating with said actuating means so that said displacement members are reciprocated between a suction stroke and a compression stroke, and fluid at the other end with said openings, for disconnecting said closed inner space from said working chambers when said cylinder ports are located on said high pressure and low pressure ports, and for connecting said closed inner space with a respective working chamber when the cylinder port of the respective working chamber is located between said high pressure and low pressure ports on said control face and as the displacement member in said respective working chamber approaches the end of its'suction stroke so that the respective working chamber is filled with fluid from said closed inner space having said predetermined pressure.
  • said actuating means reciprocates said displacement members between a first end position corresponding to the end of said suction stroke and a second end position corresponding to the end of said compression stroke in which the respective working chambers have a large volume and a small volume, respectively; and wherein said control means includes ducts in said cylinder block means connecting said working chambers with said closed inner space shortly before said displacement members reach said first end position, and being closed by said displacement members when said displacement members move out of said first end position, said dis placement members being in said first end position when the respective cylinder ports are located on said control face between the ends of said high pressure and low pressure ports.
  • said actuating means reciprocates said displacement members between a first end position corresponding to the end of said suction stroke and a second end position corresponding to the end of said compression stroke, in which the respective working chambers have a large volume and a small volume respectively; and wherein said control means include duct means in said displacement members connecting said working chambers with said closed inner space shortly before said displacement members reach said first end position, and being closed by said cylinder block means when said displacement members move out of said first end position, said displacement members being in said first end position when the respective cylinder ports are located on said control face between the ends of said high pressure and low pressure ports.
  • said hydraulic machine is an axial piston machine; wherein said actuating means is a swash plate secured to said housing means and being engaged by said free end portions of said displacement members.
  • each displacement member includes a piston axially movable in the respective working chamber, and a slide shoe movably mounted on the respective piston and forming said free end portion, said slide shoe having a face formed with a recess sliding engaging an annular circular surface portion of said swash plate; and wherein said control means include a first duct in said piston communicating with said working chamber, a second duct in said slide shoe opening into said recess, and a third duct in said swash plate connecting said annular surface portion with said closed inner space, said second and third ducts registering when said cylinder ports are located between said high pressure and low pressure ports on said control face during rotation of said cylinder block means so that fluid at said predetermined pressure flows from said closed inner space into the respective working chamber.
  • said displacement members are pistons axially movable in said working chamber, and having end faces in said working chambers located adjacent and axially outward of said ducts, respectively, in said first end positions; and wherein said ducts extend in radial directions through said cylinder block means.
  • said displacement members are pistons
  • said working chambers are cylinder chambers in which said pistons are axially movable
  • said duct means include radial ducts diametrically passing through said pistons, and axially extending ducts connecting the central portions of said radial ducts with said cylinder chambers, respectively.
  • control means include duct means connecting said closed inner space with said working chambers when the respective cylinder ports are closed by said control face, and being closed when said cylinder ports communicate with said high pressure and low pressure ports during relative rotation of said cylinder block means and said control face so that pressure fluid cannot flow into said closed inner space.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
US00240388A 1971-04-16 1972-04-03 Precharging arrangement for a hydraulic displacement machine Expired - Lifetime US3847057A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19717114577U DE7114577U (de) 1971-04-16 1971-04-16 Verdraengerpumpe

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US3847057A true US3847057A (en) 1974-11-12

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US (1) US3847057A (enExample)
CH (1) CH541722A (enExample)
DE (1) DE7114577U (enExample)
FR (1) FR2136359A5 (enExample)
GB (1) GB1346718A (enExample)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3999466A (en) * 1973-06-30 1976-12-28 Eckhard Aschke Hydrostatic pump/motor unit
US4108048A (en) * 1975-10-31 1978-08-22 Brueninghaus Hydraulik Gmbh Axial piston pump or pumping machine
US4478130A (en) * 1981-03-19 1984-10-23 Sundstrand Corporation Arrangement for slipper cavitation erosion control and impact reduction
WO1998011345A1 (de) * 1996-09-13 1998-03-19 Franz Xaver Meiller Fahrzeug- und Maschinenfabrik - GmbH & Co. KG Hydropumpe und hydromotor
EP1264985A3 (en) * 2001-06-07 2003-11-26 Caterpillar Inc. Axial piston pump with outer diameter inlet filling
US20040101419A1 (en) * 2002-11-22 2004-05-27 Caterpillar Inc. Axial piston pump with fluid bearing arrangement
US20050166751A1 (en) * 2002-09-11 2005-08-04 Bosch Rexroth Ag Hydro transformer
US20070087459A1 (en) * 2005-10-17 2007-04-19 Luminus Devices, Inc. Patchwork patterned devices and related methods
US20080019845A1 (en) * 2004-12-17 2008-01-24 Kayaba Industry Co., Ltd. Fluid Pressure Motor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014223489A1 (de) * 2014-11-18 2016-05-19 Robert Bosch Gmbh Axialkolbenmaschine

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1143681A (enExample) * 1900-01-01
US1780398A (en) * 1929-08-24 1930-11-04 Timken Axle Co Detroit Air compressor
GB684551A (en) * 1944-10-30 1952-12-17 Ludw Von Roll Schen Eisenwerke Improvements in hydraulic pumps or motors
US2642809A (en) * 1946-02-15 1953-06-23 Denison Eng Co Hydraulic apparatus
US2821932A (en) * 1954-04-28 1958-02-04 Siam Fluid pumps or engines of the piston type
US3089426A (en) * 1958-09-17 1963-05-14 New York Air Brake Co Engine
US3289606A (en) * 1964-03-20 1966-12-06 Bosch Gmbh Robert Axial piston pump or motor arrangement
US3585901A (en) * 1969-02-19 1971-06-22 Sundstrand Corp Hydraulic pump
US3609970A (en) * 1970-03-06 1971-10-05 Abex Corp Hydraulic power transfer method and apparatus
US3616726A (en) * 1970-04-02 1971-11-02 Sperry Rand Corp Power transmission
US3744377A (en) * 1971-04-12 1973-07-10 J Lauck Hydraulic motor drive

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1143681A (enExample) * 1900-01-01
US1780398A (en) * 1929-08-24 1930-11-04 Timken Axle Co Detroit Air compressor
GB684551A (en) * 1944-10-30 1952-12-17 Ludw Von Roll Schen Eisenwerke Improvements in hydraulic pumps or motors
US2642809A (en) * 1946-02-15 1953-06-23 Denison Eng Co Hydraulic apparatus
US2821932A (en) * 1954-04-28 1958-02-04 Siam Fluid pumps or engines of the piston type
US3089426A (en) * 1958-09-17 1963-05-14 New York Air Brake Co Engine
US3289606A (en) * 1964-03-20 1966-12-06 Bosch Gmbh Robert Axial piston pump or motor arrangement
US3585901A (en) * 1969-02-19 1971-06-22 Sundstrand Corp Hydraulic pump
US3609970A (en) * 1970-03-06 1971-10-05 Abex Corp Hydraulic power transfer method and apparatus
US3616726A (en) * 1970-04-02 1971-11-02 Sperry Rand Corp Power transmission
US3744377A (en) * 1971-04-12 1973-07-10 J Lauck Hydraulic motor drive

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3999466A (en) * 1973-06-30 1976-12-28 Eckhard Aschke Hydrostatic pump/motor unit
US4108048A (en) * 1975-10-31 1978-08-22 Brueninghaus Hydraulik Gmbh Axial piston pump or pumping machine
US4478130A (en) * 1981-03-19 1984-10-23 Sundstrand Corporation Arrangement for slipper cavitation erosion control and impact reduction
WO1998011345A1 (de) * 1996-09-13 1998-03-19 Franz Xaver Meiller Fahrzeug- und Maschinenfabrik - GmbH & Co. KG Hydropumpe und hydromotor
EP1264985A3 (en) * 2001-06-07 2003-11-26 Caterpillar Inc. Axial piston pump with outer diameter inlet filling
US20050166751A1 (en) * 2002-09-11 2005-08-04 Bosch Rexroth Ag Hydro transformer
US20040101419A1 (en) * 2002-11-22 2004-05-27 Caterpillar Inc. Axial piston pump with fluid bearing arrangement
US6893228B2 (en) * 2002-11-22 2005-05-17 Caterpillar Inc Axial piston pump with fluid bearing arrangement
US20080019845A1 (en) * 2004-12-17 2008-01-24 Kayaba Industry Co., Ltd. Fluid Pressure Motor
US20070087459A1 (en) * 2005-10-17 2007-04-19 Luminus Devices, Inc. Patchwork patterned devices and related methods

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Publication number Publication date
GB1346718A (en) 1974-02-13
CH541722A (de) 1973-09-15
FR2136359A5 (enExample) 1972-12-22
DE7114577U (de) 1972-09-28

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