US3861278A - Piston for hydrostatic machines - Google Patents

Piston for hydrostatic machines Download PDF

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Publication number
US3861278A
US3861278A US347352A US34735273A US3861278A US 3861278 A US3861278 A US 3861278A US 347352 A US347352 A US 347352A US 34735273 A US34735273 A US 34735273A US 3861278 A US3861278 A US 3861278A
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United States
Prior art keywords
piston
plug
filter
fluid
axial
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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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US347352A
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English (en)
Inventor
Franz Forster
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Linde GmbH
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Linde GmbH
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Publication date
Application filed by Linde GmbH filed Critical Linde GmbH
Priority to US499529A priority Critical patent/US3915071A/en
Application granted granted Critical
Publication of US3861278A publication Critical patent/US3861278A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons

Definitions

  • An axial-piston machine such as an axial-piston pump or axial-piston motor, may have a cylinder drum which is rotatable relative to a control surface or rotatable with a control surface inclined to the axis of the drum to displace axially inwardly and outwardly a plurality of pistons extending parallel to the drum axis in respective bores.
  • the cylinder bores usually disposed in angularly equispaced relationship about the axis of the cylinder drum, open at one axial end of the cylinder drum to ward a fluid-distribution plate or other member having inlet and outlet passages selectively communicating with the cylinder bores.
  • the system is driven by an external energy source, e.g. an electric or combustion motor or engine so that the pistons are displaced within their cylinder bores from a position of maximum cylinder expansion to a position of maximum contraction in a cyclical manner, each reduction in size of each of the cylinder chambers displacing fluid from the pump through the outlet or high pressure passage thereof to a load.
  • the chambers expand and a fluid me dium is drawn into the cylinder chambers from an intake or low pressure port forming the inlet to the system.
  • the fluid medium is forced into the cylinder bores at one side to rotate the cylinder drum or an inclined plate against which the motor pistons react, while fluidis discharged at the opposite side.
  • Axial-piston machines may be coupled together to provide variable-speed and variable-torque transmissions, the displacement of the pump or motor being a function of the angle at which the control plate or surface is inclined to theaxis of the cylinder drum.
  • the machines may be joined in a single housing or may be separated from one another by a considerable distance, being connected in substantially a closed hydraulic system by suitable conduits.
  • a single pump may be hydraulically coupled to a number of motor or a plurality of pumps may drive one or more motors collectively or individually.
  • the axial piston is provided with a bore extending generally over its length between the working face of the piston and the end thereof swivelably received in the shoe.
  • a fluid cushion of this type is highly advantageous, but fraught with various problems.
  • the hydraulic medium within the piston bore which is somewhat compressible, causes a lag (when the piston is made hollow) between the development of the working pressure in the cylinder bore and the transmission of pressure to the interface at which a fluid cushion is required.
  • This disadvantage may be overcome by partially filling the piston, which is made hollow to reduce its mass and hence the inertia of the system, with a body of a material having a lower specific gravity or density than the material of the piston which was originally hollow and which constitutes the outer portion of the piston. While this has the effect of increasing slightly the mass of the piston above a similarly constructed piston which is hollow, the use of lightweight materials (e.g. aluminum, magnesium or synthetic resins) within the piston bodies, where these materials are not in contact with any wear-inducing surfaces, permits the passage volume between the working end of the piston and the fluid cushion to be reduced and the lag in the development of the fluid cushion to be diminished to the point that it is not material. Consequently, the increase in mass is outweighed by the increase in the response of the fluid cushion.
  • lightweight materials e.g. aluminum, magnesium or synthetic resins
  • Another object of the invention is to provide an axialpiston machine in which disruptions and repairs resulting from the presence of contaminants in the working fluid are avoided at the juxtaposed relatively displaceable surfaces in the end of a piston for an axial-piston machine, remote from the working face of the piston.
  • Still another object of the invention is to provide a piston for an axial-piston machine which increases the useful life of the latter.
  • the working medium in such machines generally is passed through a filter and that the filter provided in each of the axial pistons is not to be considered a substitute for the main filter through which the greater part of the hydraulic medium is continuously circulated.
  • the first or main filtering action takes place in the hydraulic path-fluid power while the secondary filtering operation operates only on the minor quantities of the hydraulic medium transversing the axial pistons. Since the fluid diverted from the power path eventually becomes a leakage fluid, particles which are not entrained in the path of the main circulation remain for prolonged periods in the medium outside of this path in prior art axial-piston machine, but are removed by the piston filters in accordance with the present invention.
  • the closed-circuit machine also may circulate contaminated fluid for long periods without contact with a main filter.
  • the filter provided in each of the axial pistons removes the contaminants (e.g. metal particles), before they reach locations at which damage to the machine may be caused. In other words, the contaminant particles are prevented from reaching either the constriction in the passages of the axial pistons or the interface between the axial piston and its shoe and/or between the shoe and the control surface or plate.
  • the contaminants e.g. metal particles
  • all or part of the constriction or throttling effect required along the passage may be formed by the filter.
  • a filter eg a ware screen
  • a multiplieity of openings, perforations or the like while having the same throttling effect as a small-diameter bore, can be employed in spite of the fact that contaminant particles collect upon the filter because numerous other pathways through the filter are afforded even though some of the openings may be blocked.
  • the life span of the filter i.e., the period for which the machine can be operated until the filter of the axial piston is blocked and the pressure cushion at the interface deteriorates, is selected so as to be equal to or greater than the useful life of the machine as a whole, so that no interruption of service is necessary to clear the filter.
  • the filter may be made removable if replacement of the piston is contemplated.
  • the useful life of the filter can be made a maximum when the filter area is relatively large and, to this end, it is preferred to provide the filter as a sleeve extending axially over the major part of the length of the piston and preferably over substantially the entire length thereof from the effective piston face to the joint at which the piston engages the shoe.
  • the piston is hollow, i.e., provided with a cylindrical compartment extending substantially the full length of the filter and terminating at the working face of the piston and, is filled with a body of low specific gravity or density as described.
  • This body may be a plug which is received within the interior of the piston and carries the filter or retains the latter in place within the cylinder.
  • the sleeve of the filter screen fits snugly around the generally cylindrical plug or low specific gravity, the plug being provided with a pair of cylindrical shoulders at its end carrying the screen. Between the shoulders and within the screen, there is a generally cylindrical space with which radial bores at one end of the plug communicate, the radial bores opening into an axial inlet at the end of the plug corresponding to the working face of the piston. At the opposite end, the plug is also provided with radial bores which communicate with an axial outlet leading to the cushion region or interface.
  • the interior wall of the axial piston is preferably provided with a cylindrical recess into which the fluid can pass outwardly from the chamber surrounded by the filter screen.
  • the plug or filter body may itself be porous to constitute the filter.
  • no filter screen is necessary although the filter screen may also be employed.
  • the axial piston should be provided with passages directing the fluid generally radially as it is forced through the piston.
  • FIG. 1 is an axial cross-sectional flow through a piston according to the present invention
  • FIG. 2 is an axial cross-sectional view through another piston
  • FIG. 3 is a diagrammatic elevational view, partly broken in a way of hydraulic machine according to the invention.
  • a hydrostatic system employing the present invention may include a housing forming a sump 51 at the bottom thereof for leakage hydraulic medium, in which a hydrostatic pump 52 and a hydrostatic motor 53 are mounted.
  • the hydrostatic pump 52 compries a stationary plate 54 against which a fluid-distribution plate 55 is held by the axial pressure member thereon by a cylinder drum 56.
  • the cylinder drum axially bears upon the fluid distribution plate 55 as described, for example, in U.S. Pat. Nos. 3,292,552 and 3,495,542.
  • the cylinder 56 is formed with angularly equispaced cylinder bores 57 opening at their right hand ends toward the plate 55 and successively registering with the ports 58 thereon.
  • Each of the cylinder bores 57 slidably receives a piston 59 which is axially reciprocal within the respective bore and has a bore-shaped head 60 swivelably received in a sliding shoe 61 bearing against a nonrotatable angular control plate 62.
  • the piston is constructed as described in connection with FIG. 1.
  • the control plate 62 is swingable about an axis 63 perpendicular to the axis 64 of the drum and is formed with a central clearance through which the drive shaft 65 extends.
  • the shaft 65 which projects from the housing 50, is connected to the culinder drum 56 to rotate the latter.
  • the high pressure side or outlet 66 of the pump is connected via a filter 67 with the intake porton 68 of the hydrostatic motor 53 while the low pressure side 69 thereof is returned to the intake port 70 of the pump.
  • the main filter may, of course, be disposed in the return line as represented diagrammatically at 71.
  • the hydrostatic motor 53 comprises a plate 72 formed with the inlet and outlet parts, the fluid distribution plate 73, a cylinder barrel 74 and an axial piston 75 acting upon the inclined plate 76 which is connected with the shaft 77 to rotate the latter.
  • the principles of such pumps and motors are described at pages 109-112 and 199-200 of FLUID POWER, US. Government Printing Office, Washington, DC. 1966.
  • the cylinder drum 56 is entrained to carry the pistons 59 around the axis 64 relative to the control plate 62 which remains stationary.
  • the pistons are urged inwardly or permitted to move outwardly, thereby varying the fluid volume of the cylinder bores and displacing fluid to the motor.
  • the fluid entering the cylinder bores of the latter urge the pistons outwardly and thus rotate the motor assembly whose control plate angle can be similarly adjusted by means not illustrated but conventional in the'art.
  • thepistons 59 and 75 are provided with passages adapted to form fluid cushions at theappropriate interfaces, the fluid from these cushions eventually collecting in the sump 51 as represented by the arrows L.
  • the pistons of the machine of FIG. 3 preferable are constituted as described in connection with FIG. 1 which shows a piston 1 having an axially extending cavity 2 receiving a generally cylinder filler body 3 or plug of a material whose specific gravity is less than that of the material from which the piston 1 is constructed.
  • thefiller body may be composed of a synthetic resin resistant to attack by the hydraulic medium or a low-density metal such as aluminum or magnesium.
  • the plug 3 is held in place by a slide ring 4 which is received in an inwardly open circulational groove at the end of the cavity 3 of the working side of the piston.
  • the piston At its end adapted to project from the cylinder body, the piston is provided with a ball-shaped head 5 swivelably received in a sliding shoe 6 which is adapted to slide relative to the surface of a control plate 7 (e.g. member 62 of FIG. 3).
  • the shoe 6 is formed with a recess 8 opening in the direction of the member 7 and communicating via an axially extending bore 9 in this shoe, with an axial bore 10 through the head of the piston.
  • a hydraulic pressure cushion is provided between the faces of the shoe 6 and member 7 which serves to urge the pistons axially inwardly toward the-cylinder drum and provide a lubricated interface between these two relatively slidable members 6 and 7.
  • a similar cushion may form between the shoe 6 and the head 5.
  • the plug 3 is formed with a central bore 11 at the working end of the piston, the bore 11 being relatively short and terminating at this end in a plurality of radial bores 12 which open outwardly ahead of an angular shoulder 3a of the plug 3.
  • the plug 3 is provided with another angular shoulder 15 defining with the first mentioned shoulder 3a, an angular cylinder groove 13 into which the radial bores 12 open.
  • a cylinder filter screen 14 which is mounted at its ends upon the shoulders 3a and 15 and is clamped between these shoulders and the wall of the cavity 2.
  • the shoulder 15 is provided with grooves parallel to the piston axis which enable the fluid to enter an angular outwardly open groove 16 from which radial bores 17 deliver the fluid to an axial bore 18 of the plug regis tering and communicating with the bore 10.
  • the cavity 2 is formed with an angular recess 2a along the length of the filter so that, when the piston is displaced within its bore (see FIG. 3), a pressure at the working end forces the hydraulic medium through axial bore 11 radial bores 12, chamber 13, the perforation in the filter screen 14, the chamber 2a surrounding the filter screen, the angular groove 16, the radial bores 17 and the axial bore 18 to the constriction formed by the bore 10, whence the fluid forms a pressure cushion as described previously.
  • the plug is constituted as the filter directly.
  • the piston 101 is formed with a central cavity 102 receiving the plug 103 which is held in place by a slide ring 104.
  • the porous plug is composed of sintered metal (e.g. sintered aluminum) or another material having a low specific gravity, and serves as the filter, although a screen of the type in FIG. -1 can also be used.
  • the plug 103 is composed of cylindrical smallportions 103 between large-diameter portions 103" so that, when fluid is forced into the body through the bore 111 and then passes through the anular compartments 113a, 113b, etc.
  • the fluid passes through the large diameter portions 103" (arrows B) and/or radially through the small diameter portions 103' as represented by arrow C, eventually passing through the central bore 118 thence to the head of the piston as previously described.
  • the plug forms both the filter and the constriction.
  • a piston for an axial-piston hydrostatic machine wherein said piston at one end reacts against a surface and defines a pressure cushion therewith while the other end of the piston is receivable in a cylinder, said piston comprising an elongated body formed with a passage extending between said ends and delivering fluid under pressure to said cushion;
  • a contaminant-removing filter in said body along said passage, said body being formed with an elongated cavity between said ends;
  • a plug of a material having a lower specific gravity than that of said body received in said cavity and at least partially forming said passage said plug being formed with an inlet opening at said other end, said plug defining within said cavity an axially extending annular chamber communicating with said inlet, said filter being formed as a sleeve surrounding said plug and partitioning said chamber into two compartments communicating through said sleeve, said plug being formed at an end thereof proximal to said cushion with an outlet communicating with said chamber and feeding fluid therefrom to said cushion, said fluid within said chamber passing between said compartment from said inlet to said outlet through said sleeve.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
US347352A 1972-07-28 1973-04-02 Piston for hydrostatic machines Expired - Lifetime US3861278A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US499529A US3915071A (en) 1972-07-28 1974-08-22 Piston for hydrostatic machines

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2237240A DE2237240A1 (de) 1972-07-28 1972-07-28 Kolben fuer hydrostatische kolbenmaschinen

Publications (1)

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US3861278A true US3861278A (en) 1975-01-21

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US347352A Expired - Lifetime US3861278A (en) 1972-07-28 1973-04-02 Piston for hydrostatic machines

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JP (1) JPS4952304A (de)
DE (1) DE2237240A1 (de)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3945303A (en) * 1973-10-10 1976-03-23 Sulzer Brothers Ltd. Hydrostatic piston machine
US3986439A (en) * 1974-11-25 1976-10-19 Deere & Company Piston and slipper arrangement for hydraulic pump or motor
US3999468A (en) * 1972-12-21 1976-12-28 Caterpillar Tractor Co. Piston for hydraulic translating unit
US4191095A (en) * 1976-11-26 1980-03-04 Linde Ag Hollow piston for hydrostatic machines
US20070125227A1 (en) * 2003-09-10 2007-06-07 Josef Beck Tubular piston for a piston engine and method of manufacturing the same
US20100224057A1 (en) * 2009-03-06 2010-09-09 Mark Andrew Brown J-ME modular, internally shifting, double acting, linear fluid actuator system
US20160273653A1 (en) * 2013-02-07 2016-09-22 Kawasaki Jukogyo Kabushiki Kaisha Piston
US20190072181A1 (en) * 2017-09-05 2019-03-07 Vianney Rabhi Hydraulic piston with cooling and lubrication valve
US20210148343A1 (en) * 2019-11-15 2021-05-20 Danfoss A/S Hydraulic piston machine
US11754059B2 (en) 2019-11-15 2023-09-12 Danfoss A/S Piston of a hydraulic machine and hydraulic piston machine
US11828274B2 (en) * 2022-03-02 2023-11-28 Danfoss A/S Piston of a hydraulic piston machine

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2300009A (en) * 1937-09-15 1942-10-27 Waterbury Tool Co Power transmission
US3056358A (en) * 1960-01-20 1962-10-02 United Aircraft Corp Axial piston pump with balanced radial bearing
US3066609A (en) * 1959-11-16 1962-12-04 Sundstrand Corp Piston return mechanism
US3113491A (en) * 1960-06-18 1963-12-10 Guldner Motoren Werke Aschaffe Piston for a piston pump
US3187644A (en) * 1963-08-19 1965-06-08 Sundstrand Corp Hydraulic pump or motor device pistons
US3354786A (en) * 1960-12-21 1967-11-28 Chamberlain Ind Ltd Hydraulic motors
US3741077A (en) * 1972-04-24 1973-06-26 Eaton Corp Piston assembly

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1033028B (de) * 1956-08-09 1958-06-26 Georg Wiggermann Hydrostatische Kolbenmaschine
GB928587A (en) * 1959-04-16 1963-06-12 Council Scient Ind Res Improvements in hydraulic pumps or motors
SE319688B (de) * 1967-04-10 1970-01-19 Mannesmann Meer Ag

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2300009A (en) * 1937-09-15 1942-10-27 Waterbury Tool Co Power transmission
US3066609A (en) * 1959-11-16 1962-12-04 Sundstrand Corp Piston return mechanism
US3056358A (en) * 1960-01-20 1962-10-02 United Aircraft Corp Axial piston pump with balanced radial bearing
US3113491A (en) * 1960-06-18 1963-12-10 Guldner Motoren Werke Aschaffe Piston for a piston pump
US3354786A (en) * 1960-12-21 1967-11-28 Chamberlain Ind Ltd Hydraulic motors
US3187644A (en) * 1963-08-19 1965-06-08 Sundstrand Corp Hydraulic pump or motor device pistons
US3741077A (en) * 1972-04-24 1973-06-26 Eaton Corp Piston assembly

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3999468A (en) * 1972-12-21 1976-12-28 Caterpillar Tractor Co. Piston for hydraulic translating unit
US3945303A (en) * 1973-10-10 1976-03-23 Sulzer Brothers Ltd. Hydrostatic piston machine
US3986439A (en) * 1974-11-25 1976-10-19 Deere & Company Piston and slipper arrangement for hydraulic pump or motor
US4191095A (en) * 1976-11-26 1980-03-04 Linde Ag Hollow piston for hydrostatic machines
US20070125227A1 (en) * 2003-09-10 2007-06-07 Josef Beck Tubular piston for a piston engine and method of manufacturing the same
US7650829B2 (en) * 2003-09-10 2010-01-26 Brueninghaus Hydromatik Gmbh Tubular piston for a piston engine and method of manufacturing the same
US20100224057A1 (en) * 2009-03-06 2010-09-09 Mark Andrew Brown J-ME modular, internally shifting, double acting, linear fluid actuator system
US20160273653A1 (en) * 2013-02-07 2016-09-22 Kawasaki Jukogyo Kabushiki Kaisha Piston
US20190072181A1 (en) * 2017-09-05 2019-03-07 Vianney Rabhi Hydraulic piston with cooling and lubrication valve
US10634246B2 (en) * 2017-09-05 2020-04-28 Vianney Rabhi Hydraulic piston with cooling and lubrication valve
US20210148343A1 (en) * 2019-11-15 2021-05-20 Danfoss A/S Hydraulic piston machine
US11754059B2 (en) 2019-11-15 2023-09-12 Danfoss A/S Piston of a hydraulic machine and hydraulic piston machine
US11952987B2 (en) * 2019-11-15 2024-04-09 Danfoss A/S Hydraulic piston machine
US11828274B2 (en) * 2022-03-02 2023-11-28 Danfoss A/S Piston of a hydraulic piston machine

Also Published As

Publication number Publication date
JPS4952304A (de) 1974-05-21
DE2237240A1 (de) 1974-02-07

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