US3866517A - Rotor centering arrangement for a hydraulic machine - Google Patents

Rotor centering arrangement for a hydraulic machine Download PDF

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Publication number
US3866517A
US3866517A US305955A US30595572A US3866517A US 3866517 A US3866517 A US 3866517A US 305955 A US305955 A US 305955A US 30595572 A US30595572 A US 30595572A US 3866517 A US3866517 A US 3866517A
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United States
Prior art keywords
grooves
control ports
rotor
arrangement
control
Prior art date
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
Application number
US305955A
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English (en)
Inventor
Ulrich Aldinger
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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 US3866517A publication Critical patent/US3866517A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0435—Particularities relating to the distribution members
    • F03C1/0438—Particularities relating to the distribution members to cylindrical distribution members
    • 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
    • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
    • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
    • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
    • F01B13/061—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders
    • 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
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • F04B1/0456—Cylindrical

Definitions

  • ABSTRACT Freeh Assistant Examiner-Gregory Paul LaPointe Attorney, Agent, or Firm-Micha el S. Striker [57] ABSTRACT
  • the rotor of a radial piston pump, or motor rotates on a stationary cylindrical control body, and has chamber ports communicating with expanding and contracting working chambers, and opening on the cylindrical inner rotor surface so as to move over high pressure and low pressure control ports on the outer cylindrical control body surface. Pairs of grooves are provided on the control body surface on opposite sides of the control ports to collect leakage fuid, and the pressure in the grooves is equalized by ducts connecting pairs of grooves.
  • the present invention relates to a rotor centering arrangement for a radial piston pump or motor with a cylindrical rotor mounted on a journal and having radial cylinder bores in which pistons are reciprocated by means of an eccentric cam ring engaging the outer ends of the pistons.
  • chamber ports communicating with the working chambers in the cylinders move over high pressure and low pressure control ports in the journal or control body so that fluid is supplied to the working chambers.
  • German OS 1,453,629 discloses a radial piston machine in which grooves are provided on the side of a port on the control body which are connected with a diametrically opposite control port by a duct. This results in a pressure area in the region of the grooves laterally of the low pressure control port, while on the opposite side, the pressure area extends only from the high pressure control port over the comparatively narrow sealing portion to the respective groove in which the pressure is reduced to low pressure.
  • the pressure area compensates on the rotor the pressures acting in the region of the control ports, while hydrodynamic pressure areas form between the ends of the control ports so that the forces acting on the rotor in this region are equalized.
  • Another object of the invention is to provide grooves around the control body in which the same pressure prevails so that the rotor is supported on the control body in a centered position.
  • the present invention provides two pressure grooves on opposite sides of each control port, and a connecting duct connecting the pairs of grooves located on the same side of the control port.
  • the arrangement of the invention has the advantage that the pressure fluid leaking through the clearance or gap between the outer cylindrical surface of the control body and the inner cylindrical surface of the rotor, is uniformly distributed so that the pressure areas which develop, are symmetrical.
  • the lubrication between the engaging surfaces is improved.
  • FIG. 1 is a longitudinal sectional view illustrating a radial piston machine provided with the improvement of the present invention.
  • FIG. 2 is a cross-sectional view taken on line [MI in FIG. 1.
  • a radial piston machine has a housing I which is closed by housing cover 2.
  • a hollow rotor 5 has an inner blind bore forming an inner rotor surface 6 in sliding engagement with an outer cylindrical surface 3 of a control body or journal 4.
  • One end of the rotor 5 is also mounted in a bearing 7 secured to the housing 1.
  • the rotor 5 has substantially radial cylindrical bores 8 in which pistons 9 are mounted for inward and outward reciprocating movement, forming in cylinders 8, expanding and contracting working chambers 8a opening in circumferentially spaced chamber ports 8b on the inner surface 6 of rotor 5.
  • the pistons 9 have slide shoes 10 at the outer ends which have balls 10a forming a joint with seats 9a in pistons 9.
  • the slide shoes 10 slide on the inner endless surface 11 of an eccentric actuator cam ring 12 whose eccentricity can be adjusted by screwing a spindle 14 into a nut 13 secured to the outside of the cam ring 12.
  • a hand wheel 16 is used for turning spindle 14, which is held immovable in axial direction by a bearing provided in a bracket on housing 1.
  • the adjustment of the eccentricity of cam ring 12 results in different strokes of the pistons 9, 11 in the cylinders 8 so that the working chambers 8a expand and contract for receiving or discharging fluid through the chamber ports 8b which are arranged circumferentially spaced on the inner surface 6.
  • the downward movement of the cam ring 12 by the operation of the hand wheel 16, is opposed by spring 17 abutting cam ring 12 and housing 1.
  • the control body 4 has two diametrically opposed high pressure and low pressure control ports 20, 21, each of which is connected in the control body 4 by transverse passages 22, 23' with axi ally extendinghigh pressure and low pressure conduits 22 and 23, see also FIG. 1.
  • pairs 24, and 26, 27 of narrow partcircular diametrically arranged grooves 24 to 27 are formed in the outer cylindrical surface of the control body 4.
  • the pair of grooves 24, 25 is located on one side of the control ports 20, 21, and a pair of grooves 26, 27 is located on the other side of control ports 20, 21, the grooves being axially spaced from the control ports between the same, as best seen in FIG. 1.
  • the grooves 24, 25 of one pair, and the grooves 26, 27 of the other pair, are respectively connected by straight ducts 28 and 29 which open near the ends of the respective grooves connected thereby.
  • the ends of the grooves of the same pair are spaced from each other, and the ends of the control ports 20 and 21 are also spaced from each other, the ends of the control ports 20, 21 being axially aligned with the respective ends of from the control ports.
  • the slide shoes slide on the inner surface 11 of the eccentric cam ring 12 and force the pistons 9 to reciprocate so that fluid is sucked from the control port 20, for example, and discharged into the control port 21.
  • the length of the stroke of pistons 9, by which the volume of the working chambers 8a is increased and reduced, can be adjusted by displacing the actuating cam ring 12 by operation of hand wheel 16.
  • the disclosed embodiment comprises a rotor 5 having circumferentially spaced working chambers 8a for a fluid and an inner surface 6 having a set of chamber ports 8b communicating with the working chambers 8a, respectively, and moving during rotation of rotor 5 along a circular path; and a stationary control body having an outer surface 3 in sliding contact with the inner control surface for supporting the rotor 5, and having in the outer surface 3 a pair of diametrically disposed part-circular control ports 20, 21 located in the path of the chamber ports 8 and being supplied with high pressure and low pressure fluid through conduits 22, 23, 22', 23' opening in the control ports 20, 21.
  • the control body 4 has first and second pairs 24, 25 and 26, 27 of diametrically disposed part-circular grooves, the first and second pairs of grooves 24, 25 and 26, 27 being located at opposite sides of the control ports 20, 21 spaced a small axial distance from the same so that leakage from the control ports 20, 21 flowing through the clearance between the outer and inner surfaces 3, 6, fills the first and second pairs of grooves 24 to 27.
  • the control body 4 has first and second ducts 28, 29 located on opposite sides of the pair of control ports 20, 21 and connecting the grooves of the first and second pairs of grooves 24, 25 and 26, 27, respectively, whereby uniform pressure prevails in the first and second pairs of grooves 24, 25 and 26, 27 and between the outer and inner surfaces 3, 6.
  • a rotor centering arrangement for a hydraulic machine comprising, in combination, a rotor having a set of circumferentially spaced working chambers for a fluid, and an inner circumferential surface having a set of chamber ports communicating with respective ones of said working chambers and moving during rotation along a circular path; and a stationary control body having an outer circumferential surface in sliding contact with said inner circumferential surface of said rotor, and being provided in said outer circumferential surface with a pair of diametrically oppositely disposed part-circular control ports located along said path, said control body having high and low pressure conduits opening into respective ones of said control ports, so that during rotation of said rotor low pressure and high pressure fluid alternately enter said working chambers, said control body having first and second pairs of diametrically oppositely disposed part-circular grooves, said first and second pairs of grooves being located on opposite axial sides of said control ports spaced axially from the latter so that leakage fluid from said control ports flowing through the radial clearance between said outer and inner circum
  • control ports having circumferentially spaced ends separated by portions of said outer surface; and wherein said grooves of said first and second pairs of grooves have circumferentially ends spaced by portions of said outer surface.
  • said high pressure conduit and low pressure conduit have axially extending portions located in a plane passing between the circumferentially spaced ends of said grooves and control ports, and transverse portions connecting said axially extending portions with said control ports, respectively; and wherein. said straight ducts cross said plane at right angles.
  • control ports have a substantially greater axial width than said grooves, respectively.
  • control ports have a greater radial depth than said grooves; and said control ports have a substantially greater axial width than said grooves, respectively.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
US305955A 1971-12-10 1972-11-13 Rotor centering arrangement for a hydraulic machine Expired - Lifetime US3866517A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE7146528 1971-12-10

Publications (1)

Publication Number Publication Date
US3866517A true US3866517A (en) 1975-02-18

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ID=6625651

Family Applications (1)

Application Number Title Priority Date Filing Date
US305955A Expired - Lifetime US3866517A (en) 1971-12-10 1972-11-13 Rotor centering arrangement for a hydraulic machine

Country Status (6)

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US (1) US3866517A (ja)
JP (1) JPS5514271B2 (ja)
CH (1) CH549161A (ja)
FR (1) FR2164373A5 (ja)
GB (1) GB1384430A (ja)
IT (1) IT971383B (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4034653A (en) * 1975-02-03 1977-07-12 Anderson Arthur F Axial piston motor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57113501A (en) * 1980-12-29 1982-07-15 Matsushita Electric Works Ltd Ceiling illuminating system

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1925378A (en) * 1931-04-01 1933-09-05 Oilgear Co Pump
US2021353A (en) * 1934-03-05 1935-11-19 Hydraulic Press Mfg Co Hydraulic pump or motor
US2430753A (en) * 1943-11-08 1947-11-11 Ziska Adam Pump
US2972311A (en) * 1956-12-19 1961-02-21 Gen Motors Corp Pump or motor
US3171361A (en) * 1961-08-19 1965-03-02 Sarl Rech S Etudes Production Multi-cylinder hydraulic pumps especially of piston-chamber type
US3199460A (en) * 1962-01-11 1965-08-10 Stewart Warner Corp Hydraulic pump or motor
US3199461A (en) * 1963-05-27 1965-08-10 Cessna Aircraft Co Hydraulic pump or motor
US3232239A (en) * 1962-01-26 1966-02-01 Lely Nv C Van Der Hydraulic pumps and motors

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1925378A (en) * 1931-04-01 1933-09-05 Oilgear Co Pump
US2021353A (en) * 1934-03-05 1935-11-19 Hydraulic Press Mfg Co Hydraulic pump or motor
US2430753A (en) * 1943-11-08 1947-11-11 Ziska Adam Pump
US2972311A (en) * 1956-12-19 1961-02-21 Gen Motors Corp Pump or motor
US3171361A (en) * 1961-08-19 1965-03-02 Sarl Rech S Etudes Production Multi-cylinder hydraulic pumps especially of piston-chamber type
US3199460A (en) * 1962-01-11 1965-08-10 Stewart Warner Corp Hydraulic pump or motor
US3232239A (en) * 1962-01-26 1966-02-01 Lely Nv C Van Der Hydraulic pumps and motors
US3199461A (en) * 1963-05-27 1965-08-10 Cessna Aircraft Co Hydraulic pump or motor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4034653A (en) * 1975-02-03 1977-07-12 Anderson Arthur F Axial piston motor

Also Published As

Publication number Publication date
CH549161A (de) 1974-05-15
FR2164373A5 (ja) 1973-07-27
GB1384430A (en) 1975-02-19
IT971383B (it) 1974-04-30
JPS5514271B2 (ja) 1980-04-15
JPS4866206A (ja) 1973-09-11

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