US3762843A - Van type rotary hydraulic transducer - Google Patents

Van type rotary hydraulic transducer Download PDF

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Publication number
US3762843A
US3762843A US00141728A US3762843DA US3762843A US 3762843 A US3762843 A US 3762843A US 00141728 A US00141728 A US 00141728A US 3762843D A US3762843D A US 3762843DA US 3762843 A US3762843 A US 3762843A
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US
United States
Prior art keywords
pressure
rotor
fluid
vanes
recess
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
US00141728A
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English (en)
Inventor
N Suzuki
U Yuki
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Yuken Kogyo Co Ltd
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Yuken Kogyo Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Yuken Kogyo Co Ltd filed Critical Yuken Kogyo Co Ltd
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Publication of US3762843A publication Critical patent/US3762843A/en
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C15/062—Arrangements for supercharging the working space
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid

Definitions

  • ABSTRACT Vrablik AttorneySteinberg & Blake [57]
  • ABSTRACT A vane-type rotary hydraulic transducer, being a pump or a motor, in which a rotor equipped with vanes rotates within eccentric cam means which causes spaces between the vanes to expand and contract as the motor rotates, the spaces communicating with respective high and low pressure chambers when in different angular positions, and a pressure intermediate the pressures in these chambers being applied to the spaces between blades when they are positioned between said angular positions.
  • An object of the present invention is to reduce the drawbacks of conventional vane-type motors and pumps.
  • the invention provides a vane-type transducer which is so designed and arranged that the fluid gathered in a substantially annular fluid-chamber space defined by the rotor and the cam ring is exposed to an intermediate fluid pressure in the course of its volumetric expansion and contraction, the said intermediate fluid pressure being lower than the fluid pressure on the high pressure side of the transducer and higher than the fluid pressure on the low pressure side, when the transducer is located conventionally in a hydraulic circuit.
  • FIG. 1 is a longitudinal sectional view of a vane pump according to the invention, taken along line II of FIG. 4 in the direction of the arrows;
  • FIGS. 2 and 3 are front elevations of segments which make contact with respective end faces of the rotor in the pump shown in FIG. 1;
  • FIGS. 4 and 5 are partial end views of the rotor showing the vanes thereof in two operating positions, the views being taken along line IVIV of FIG. 1.
  • the vane pump shown in the Figures comprises a casing 1 having a fluid inlet opening 2 and a fluid outlet opening 3.
  • a driving shaft 4 connected to a pumpdriving motor (not shown) is rigidly connected to a rotor 5 carrying a number of blade-like vanes 7 (see FIGS. 4 and 5) round its periphery.
  • These vanes 7 are slidably received in radial slots in the rotor 5 and, when the rotor5 is set into rotation with the drive shaft 4, are urged outwards under centrifugal action into physical contact with the cam ring 6 positioned about the rotor 5, in a well-known manner.
  • blocks or segments 8, 9 shown in FIGS. 2 and 3 respectively which are provided with duct means communicating with outlet opening 3 and with a fluid pressure reducing means 10, which latter is adapted to deliver part of the exhaust fluid at a reduced pressure to the base portions of the vanes 7, as will more fully be disclosed hereinafter.
  • the exhaust fluid from the pressure reducing means 10 is delivered via duct 13 bored through the housing 1 to an annular groove formed at the exterior of seg ment 8 and communicating with two inlet ports 11 leading into a pair of sector-shaped recesses 12 formed on the end surface of the segment 8.
  • Said inlet ports 11 are connected, as shown in FIG. 2, hydraulically with four inlet ports 14 through ducts 15, said ports 14 opening at equally spaced points onto the end surface of the segment 8.
  • annular oilchamber space is defined by the rotor S and the cam ring 6, having a greater cross-section where it communicates with the low pressure chamber connected hydraulically with the inlet opening 2 and a lesser crosssection where it communicates with the high pressure chamber 18 connected hydraulically with the outlet opening 3.
  • the above-mentioned inlet ports 14 open into the zones of the said oil-chamber space having a medium cross-section, i.e., between the larger low pressure zone andthe smaller high pressure zone.
  • the fluid pressure prevailing in the enclosure or space a or b defined by two adjoining vanes 7 is kept lower than the fluid pressure at the outlet opening 3, on account of the direct fluid communication of the said enclosure a or b with the pressure reducing means 10.
  • the intermediate fluid pressure prevailing in said en closure 0, b is selected to be lower than that prevailing at the outlet opening 3 and higher than that at the inlet opening 2.
  • the intermediate fluid pressure in said enclosure 0 or b is selected to be higher than the outlet fluid pressure and lower than the inlet fluid pressure.
  • said duct 13 is kept from hydraulic communication from the intake opening 2 and the outlet opening 3, even when the vanes 7 are set into operation by rotation of the drive shaft 4.
  • numeral 17 denotes arcuate grooves on the end surface of the segment 8, which are kept by way of passages 17a (FIGS. 1 and 2) in fluid connection with the high pressure duct or chamber 18 for outlet fluid
  • numerals 19 and 20 denote pistons of the larger and lesser diameters, respectively, fitted in the pressure reducing device 10
  • numeral 21 denotes a sleeve or casing
  • numerals 22, 23 denote sleeve or casing covers
  • numeral 24 denotes a drain duct on the pump suction side communicating with the space 24a where the pistons 19 and 20 engage each other
  • Part of the outlet fluid at raised pressure is delivered into said arcuate grooves 17 on the rotor S from duct or chamber 18 through passages 17a, and also into said fluid pressure reducing means through passage 13a (FIG. 1).
  • the fluid at elevated pressure which enters into the pressure reducing means 10 through the passage 13a reaches a chamber which houses a spring at the right end of piston 20, as viewed in FIG. 1.
  • This spring acts on the piston 20 to displace the latter to the left, as viewed in FIG. 1, thus fully opening, when the parts are at rest, the bore 13 as well as a passage in the casing 21 which provides communication between the right end of the piston 20 and thee end chamber 19a which communicates with the left end of the larger piston 19.
  • the recesses 17 which receive the high pressure fluid deliver the high pressure fluid to the inner ends of the vanes 7 when they are located at the high pressure zones, so that as the vanes 7 rotate they are urged outwardly by an intermediate pressure at the low pressure zones of the pump and at a high pressure at the high pressure zones of the pump.
  • intermediate pressure recess 12 is separated from the high pressure recesses 17 only by the narrow surface areas 17b at the end surface of the segment, 8, some of the-high pressure fluid delivered through the openings 17 to the inner ends of the vanes leaks in the form of a film radially inwardly across the surface areas 17b into the intermediate pressure space 12 so that the latter is additionally supplied with fluid at an intermediate pressure byway of leakage from the openings 17.
  • Intermediate pressure outlet fluid is also supplied into said enclosures a, b through said inlet ports 14 hydraulically connected with said'ports 11 through ducts 15.
  • the fluid pressures at enclosures c, a and d are equal to the fluid suction pressure, p Ap, and p, respectively, while the fluid pressures at enclosures e, b and fare equal to p, p Ap and the fluid suction pressure (see FIGS. 4 and 5).
  • FIG. 4 illustrates how the inner ends of the rotor slots which receive the vanes 7 communicate not only with the intermediate pressure space 12 but also with the high-pressure outlets 17. Moreover, referring to FIG. 4, the fluid load applied to the vane 7a just exposed to the outlet fluid pressure is equally divided between it and the preceding vanes 7b, 7c, thus enabling the described vane pump to bear higher fluid pressures than in the case of the conventional single-stage pump.
  • vanes 7a, 7b that follow are maintained at the medium fluid pressure, thus obviating abrupt fluid pressure changes and minimizing the accompanying mechanical sounds and pulsating vane movements.
  • the structure of the invention can operate either as a pump or motor.
  • This structure includes the housing means 1, 26 formed with the high-pressure part 3 to which high pressure fluid is delivered when the structure operates as a pump and which receives high pressure fluid when the structure operates as a motor. Also, the structure is formed with the low-pressure port 2 into which fluid is sucked when the structure operates as a pump and to which fluid is delivered when the structure operates as a motor.
  • the housing means 1, 26 carries in its interior the pair of slide portions 8, 9 which have inner surfaces, respectively visible in FIGS.
  • the housing means 1, 26 including the interior slide portions 8, 9 are formed with low-pressure passages providing communication between the lowpressure port 2 and spaces between the vanes and between the rotor 5 and the cam means 6 during one part of the angular rotation of the vanes, the housing means 1, 26, including the slide portions 8, 9, also being formed with high-pressure passages communicating with the space between the rotor 5 and the cam means 6 and with the spaces between the vanes during another part of the angular movement thereof during each rotation.
  • the slide portions 8, 9 are provided at their inner surfaces which slidably engage the opposed faces of the rotor 5 with high-pressure recesses 17 which communicate directly with the high-pressure passages, such as the passagees 18, for supplying high-pressure fluid directly from the high-pressure passages to the inner ends of the vanes in the vane slots of the rotor 5 during the time that the vanes have the spaces therebetween in communication with the high-pressure passages.
  • intermediatepressure recesses 12 which also communicate with the high-pressure passages 18, but only through the pressure-reducing means 10, and these intermediate pressure recesses 12 communicate with the inner ends of the vane slots for delivering intermediate-pressure fluid thereto for urging the vanes outwardly toward the cam means at an intermediate pressure, the inner ends of the vane slots communicating with the intennediate pressure recesses only during the time that the spaces between the vanes communicate through the lowpressure passages with the low-pressure port 2.
  • intermediate pressure recesses 12 have portions situated inwardly of the high-pressure recesses 17 so that leakage fluid flows from the high-pressure recesses 17 across the surface-portions 17b of the slide portions 8, 9 into the intermediate pressure recesses 12 so that the latter are supplied with fluid at intermediate pressure also by way of leakage from the high-pressure recesses at the interface between the slide portions 8, 9 and the opposed side faces of the rotor 5.
  • housing means formed with a lowpressure port and a high-pressure port, a rotor supported for rotary movement in said housing means and having opposed side faces and being formed at its periphery with radial vane slots, a plurality of vanes situated in said slots for slidable movement radially therein, said slots extending inwardly beyond said vanes and said vanes extending outwardly beyond the periphery of said rotor, cam means situated in said housing means and surrounding said rotor, said cam means having an inner camming surface engaged by the outer tips of said vanes while they rotate with said rotor for displacing fluid between high and low pressure zones situated between said cam means and rotor, a pair of slide portions situated in said housing means and having directed toward each other slide surfaces which slidably engage said opposed side faces of said rotor,
  • said housing means being formed with a low-pressure passage communicating with a low-pressure zone between said rotor and cam means and with said lowpressure port and said housing means and slide portions being formed with a high-pressure passage communi cating with a high-pressure zone between said rotor and cam means and with said high-pressure port, said slide portions being formed with high-pressure recesses angularly aligned with said high-pressure zone and communicating directly with said high-pressure passage and with inner ends of said vane slots to deliver to the latter from the high-pressure passage fluid at high pressure to urge the vanes outwardly during the time that they travel through a high-pressure zone, and said slide portions being formed at their inner surfaces in angular alignment with said low-pressure zone with intermediate pressure recesses communicating with the inner ends of said vane slots, and pressure-reducing means carried by said housing means and communicating with said high-pressure passage for receiving high-pressure fluid therefrom, said housing means and slide portions being formed with intermediate pressure passages communicating with said pressure-reducing means and said intermediate pressure recesses, said pressure-reducing

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US00141728A 1970-07-09 1971-05-10 Van type rotary hydraulic transducer Expired - Lifetime US3762843A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP5950970 1970-07-09

Publications (1)

Publication Number Publication Date
US3762843A true US3762843A (en) 1973-10-02

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ID=13115282

Family Applications (1)

Application Number Title Priority Date Filing Date
US00141728A Expired - Lifetime US3762843A (en) 1970-07-09 1971-05-10 Van type rotary hydraulic transducer

Country Status (5)

Country Link
US (1) US3762843A (en:Method)
CA (1) CA936416A (en:Method)
DE (1) DE2132465C2 (en:Method)
FR (1) FR2097943A1 (en:Method)
GB (1) GB1334158A (en:Method)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4543049A (en) * 1983-11-04 1985-09-24 Diesel Kiki Co., Ltd. Vane compressor with means for obtaining sufficient back pressure upon vanes at the start of compressor
WO1999061798A1 (en) * 1998-05-27 1999-12-02 Apax Vehicle Developments Inc. Hydraulic pressure ratio transducer
EP1298323A3 (en) * 2001-09-27 2004-06-09 Unisia JKC Steering Systems Co., Ltd. Variable displacement pump
US20080075615A1 (en) * 2006-09-22 2008-03-27 Timothy Matthew Staton Power steering pump
US20100166588A1 (en) * 2008-12-30 2010-07-01 Heitz Steven A Vane pump with rotating cam ring and increased under vane pressure
US20180306184A1 (en) * 2015-11-02 2018-10-25 Kyb Corporation Vane pump
US12098718B2 (en) * 2021-11-03 2024-09-24 Lg Electronics Inc. Rotary compressor

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5338881Y2 (en:Method) * 1973-03-02 1978-09-20
US4207038A (en) * 1978-05-01 1980-06-10 Ford Motor Company Power steering pump
JPS5716291A (en) * 1980-07-01 1982-01-27 Sanden Corp Volume type fluid compressor
DE19631974C2 (de) * 1996-08-08 2002-08-22 Bosch Gmbh Robert Flügelzellenmaschine

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2555785A (en) * 1947-09-11 1951-06-05 Louis B Cook Amusement device embodying a simulated racing game
DE809131C (de) * 1948-11-24 1951-07-23 Gen Motors Corp Drehkolbenpumpe
US2777396A (en) * 1953-05-15 1957-01-15 American Brake Shoe Co Fluid energy translating device
US3516768A (en) * 1968-11-01 1970-06-23 Sperry Rand Corp Power transmission

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4543049A (en) * 1983-11-04 1985-09-24 Diesel Kiki Co., Ltd. Vane compressor with means for obtaining sufficient back pressure upon vanes at the start of compressor
WO1999061798A1 (en) * 1998-05-27 1999-12-02 Apax Vehicle Developments Inc. Hydraulic pressure ratio transducer
EP1298323A3 (en) * 2001-09-27 2004-06-09 Unisia JKC Steering Systems Co., Ltd. Variable displacement pump
EP1767784A1 (en) * 2001-09-27 2007-03-28 Unisia JKC Steering Systems Co., Ltd. Variable displacement pump
US20080075615A1 (en) * 2006-09-22 2008-03-27 Timothy Matthew Staton Power steering pump
US7628596B2 (en) * 2006-09-22 2009-12-08 Ford Global Technologies, Llc Power steering pump
US20100166588A1 (en) * 2008-12-30 2010-07-01 Heitz Steven A Vane pump with rotating cam ring and increased under vane pressure
US8113804B2 (en) * 2008-12-30 2012-02-14 Hamilton Sundstrand Corporation Vane pump with rotating cam ring and increased under vane pressure
US20180306184A1 (en) * 2015-11-02 2018-10-25 Kyb Corporation Vane pump
US12098718B2 (en) * 2021-11-03 2024-09-24 Lg Electronics Inc. Rotary compressor

Also Published As

Publication number Publication date
CA936416A (en) 1973-11-06
DE2132465A1 (de) 1972-01-13
FR2097943A1 (en:Method) 1972-03-03
DE2132465C2 (de) 1984-05-17
GB1334158A (en) 1973-10-17

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