US3910162A - Force compensating arrangement for a radial piston machine - Google Patents

Force compensating arrangement for a radial piston machine Download PDF

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Publication number
US3910162A
US3910162A US353625A US35362573A US3910162A US 3910162 A US3910162 A US 3910162A US 353625 A US353625 A US 353625A US 35362573 A US35362573 A US 35362573A US 3910162 A US3910162 A US 3910162A
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United States
Prior art keywords
rotor
axis
plane
resultant
ports
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Expired - Lifetime
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US353625A
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English (en)
Inventor
Gerhard Nonnenmacher
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of US3910162A publication Critical patent/US3910162A/en
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Classifications

    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/047—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the outer ends of the cylinders

Definitions

  • the rotor of a radial piston pump has cylinders, and pistons cooperating with an eccentric actuating ring so that the resultant of the inward directed forces passes through the axis of the actuator ring at an angle less than 90 to a plane through the axes of the rotor and of the actuator ring.
  • the high pressure and low pressure control ports on the control pintle supporting the rotor are angularly displaced! relative to this plane so that the resultant of outward directed pressure forces, which passes through the rotor axis, is parallel to the resultant of the inwardly directed forces, and compensates the same.
  • the present invention provides a radial piston machine in which the cylinder ports on the inner surface of the rotor are circumferentially displaced to lead the cylinders during rotation while the machine operates asa pump, for example, while the high pressure and low pressure control ports on the pintle are angularly displaced relative to a plane passing through the axes of the rotor and of the actuator ring so that the high pressure control port is moved toward the inner dead center position of the rotor in which the rotor is closest spaced from the actuator ring.
  • the inner relieving pressure area on the control pintle is turned so that its direction conforms to the resultant of the forces acting on the bearings of the rotor.
  • FIG. 1 is a schematic cross-sectional view illustrating a first embodiment of the invention
  • FIG. 2 is a schematic cross sectional view illustrating a second embodiment of the invention.
  • FIG. 3 is partially a cross-sectional view corresponding to FIG. I, and partially a diagram illustrating the inwardly directed forces produced by the eccentric actuator ring;
  • FIG. 4 is a cross-sectional view illustrating a radial piston machine according to the prior art.
  • FIG. 5 is a cross-sectional view of the embodiment of FIG. I, and including a diagrammatic illustration of the compensation of the resultant of the inwardly directed mechanical forces by the resultant of outwardly di rected pressure forces in accordance with the invention.
  • a radial piston ma has a control pintle 10 surrounded by the inner cylindrical surface 11a of a rotor 11, and supporting rotor 11 for rotation about an axis A,.
  • a stationary actuator ring 14 has an inner cylindrical surface 14a having an axis A parallel with rotor axis A and spaced therefrom the distance e representing the eccentricity of the actuator ring 14 in relation to the rotor 11.
  • Rotor 11 has six cylinders 15 with radial axes, not
  • each piston 16 passes successively through i the inner dead center point Ti and the outer dead center point Ta of plane B. Rotor 11 is closer to the actuator ring 14 at the inner dead center point Ti than at the outer dead center point Ta.
  • the cylinders 15 do not directly communicate with the control ports 12 and 13, but are connected with the same by cylinder passages 18 which have inner ports 18a sweeping the control ports 12 and 13.
  • the passages 18 are parallel to the radial axes of the respective cylinders which intersect the rotor axis A Assuming that the machine operates as a pump in the direction of the arrow 0, the axes of the cylinder passages 18 lead the axes of the respective cylinders 17.
  • the rotor passages 18' which open in ports on the inner surface llla' of rotor 11', are slanted to the radial axes of the respective cylinders 15 so that the outer end of each rotor passage 18 is concentric with the bottom face 17 while the cylinder port 18' leads the radial axis of the respective cylinder 15 in the same position as the cylinder ports 18a in the embodiment of FIG. 1.
  • FIG. 3 illustrates the embodiment of FIG. 1, but it will be understood that the diagram shown in FIG. 3 is also applicable to the embodiment of FIG. 2.
  • FIG. 4 shows a radial piston pump according to the prior art with a rotor 11' and high pressure and low pressure pressure ports 12' and 13' in the control pintle 10 which are arranged symmetrically to the plane B which passes through the axes A and A
  • the outwardly directed forces of control pindle I acting on rotor 11" have a resultant P perpendicular to the plane B and passing through axis A,. Consequently, the outwardly directly resultant P of the arrangement of the prior art, cannot fully compensate the resultant P of the inwardly directed mechanical forces, described with reference to FIG. 3.
  • control ports 12 and 13 are displaced in circumferential direction so-that the resultant vector P which passes through the axis A,, is substantially parallel to the resultant P of the inwardly directed mechanical forces. Consequently, the two opposite resultant forces P and P fully compensate each other.
  • the ports 18a are displaced relative to the cylinders 15.
  • the control ports 12 and 13 are geometrically arranged on opposite sides of a second plane E which passes through the rotor axis A at an angle to the plane B.
  • the control ports 18a may be displaced relative to the axis of the respective cylinders 15, the same angular distance.
  • the angle between the planes E and B may be the same as the angle between the plane D and the resultant force
  • the high pressure control port 12 is angularly displaced toward the inner dead center point Ti, which is determined by the position of the actuator ring 14.
  • the rotor 11 rotates in the direction of the arrow 0 shown in FIG. 1.
  • fluid under high pressure is supplied through the control pintle to the high pressure port 12 which causes rotation of the rotor 11 in the opposite counterclockwise direction.
  • Force compensating arrangement for a radial piston machine comprising a control pintle having an outer cylindrical surface formed with diametrically disposed circumferentially extending high pressure and low pressure control ports; a rotor having an inner cylindrical surface mounted on said outer cylindrical surface for rotation about a first axis, said rotor including equally angularly spaced cylinders having radial cylinder axes intersecting said first axis and cylinder ports on said inner cylindrical surface communicating with said control ports, and pistons in said cylinders; and an actuator ring surrounding said rotor and having an inner cylindrical actuator surface in sliding contact with said pistons and having a second axis, said first and said second axes being parallel and located in a first axial plane so that said rotor has in said first plane inner and outer dead centerpoints closest to, and farthest from, respectively, said actuator surface whereby a resultant of inwardly directed forces passes through said second axis defining a predetermined angle less than with said first plane in the region of said inner dead center point

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
US353625A 1972-04-22 1973-04-23 Force compensating arrangement for a radial piston machine Expired - Lifetime US3910162A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2219881A DE2219881A1 (de) 1972-04-22 1972-04-22 Radialkolbenmaschine

Publications (1)

Publication Number Publication Date
US3910162A true US3910162A (en) 1975-10-07

Family

ID=5842992

Family Applications (1)

Application Number Title Priority Date Filing Date
US353625A Expired - Lifetime US3910162A (en) 1972-04-22 1973-04-23 Force compensating arrangement for a radial piston machine

Country Status (6)

Country Link
US (1) US3910162A (cg-RX-API-DMAC10.html)
JP (1) JPS4921701A (cg-RX-API-DMAC10.html)
CH (1) CH549727A (cg-RX-API-DMAC10.html)
DE (1) DE2219881A1 (cg-RX-API-DMAC10.html)
FR (1) FR2182480A5 (cg-RX-API-DMAC10.html)
GB (1) GB1398485A (cg-RX-API-DMAC10.html)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5117936A (en) * 1989-09-18 1992-06-02 Kubota Corporation Vehicle propelling apparatus
EP1191223A1 (en) * 2000-09-26 2002-03-27 Nu-Image Packaging (Clwyd) Limited Alyn Bridge Works Apparatus for dispensing fluids
GB2348252B (en) * 1999-03-20 2003-10-15 Nu Image Packaging Apparatus for dispensing fluids
WO2009118366A1 (fr) * 2008-03-26 2009-10-01 Bia Convertisseur d'energie mecanique en energie hydraulique et robot mettant en oeuvre le convertisseur

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61295472A (ja) * 1985-06-21 1986-12-26 株式会社デンソー 冷媒受液器

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2585232A (en) * 1950-03-27 1952-02-12 Oilgear Co Pressure compensated pump
US2823619A (en) * 1956-07-16 1958-02-18 Gen Electric Radial type hydraulic unit
US3037488A (en) * 1960-01-08 1962-06-05 George M Barrett Rotary hydraulic motor
US3188918A (en) * 1962-04-04 1965-06-15 Soya Rederi Ab Rotary machine having a fluidworking medium
US3192867A (en) * 1959-06-15 1965-07-06 Dentatus Ab Machine adapted to operate as pump, compressor or motor
US3408948A (en) * 1966-12-12 1968-11-05 Eaton Yale & Towne Positioning of control ring

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2585232A (en) * 1950-03-27 1952-02-12 Oilgear Co Pressure compensated pump
US2823619A (en) * 1956-07-16 1958-02-18 Gen Electric Radial type hydraulic unit
US3192867A (en) * 1959-06-15 1965-07-06 Dentatus Ab Machine adapted to operate as pump, compressor or motor
US3037488A (en) * 1960-01-08 1962-06-05 George M Barrett Rotary hydraulic motor
US3188918A (en) * 1962-04-04 1965-06-15 Soya Rederi Ab Rotary machine having a fluidworking medium
US3408948A (en) * 1966-12-12 1968-11-05 Eaton Yale & Towne Positioning of control ring

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5117936A (en) * 1989-09-18 1992-06-02 Kubota Corporation Vehicle propelling apparatus
GB2348252B (en) * 1999-03-20 2003-10-15 Nu Image Packaging Apparatus for dispensing fluids
EP1191223A1 (en) * 2000-09-26 2002-03-27 Nu-Image Packaging (Clwyd) Limited Alyn Bridge Works Apparatus for dispensing fluids
WO2009118366A1 (fr) * 2008-03-26 2009-10-01 Bia Convertisseur d'energie mecanique en energie hydraulique et robot mettant en oeuvre le convertisseur
FR2929347A1 (fr) * 2008-03-26 2009-10-02 Bia Soc Par Actions Simplifiee Convertisseur d'energie mecanique en energie hydraulique et robot mettant en oeuvre le convertisseur
US20110085922A1 (en) * 2008-03-26 2011-04-14 Bia Converter for Converting Mechanical Energy Into Hydraulic Energy and Robot Implementing Said Converter
CN102027234A (zh) * 2008-03-26 2011-04-20 岜公司 将机械能转换为液压能的转换器和采用该转换器的机器人
CN102027234B (zh) * 2008-03-26 2014-04-16 岜公司 将机械能转换为液压能的转换器和采用该转换器的机器人
US8734123B2 (en) 2008-03-26 2014-05-27 Bia Converter for converting mechanical energy into hydraulic energy and robot implementing said converter

Also Published As

Publication number Publication date
FR2182480A5 (cg-RX-API-DMAC10.html) 1973-12-07
JPS4921701A (cg-RX-API-DMAC10.html) 1974-02-26
GB1398485A (en) 1975-06-25
CH549727A (de) 1974-05-31
DE2219881A1 (de) 1973-10-25

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