US3401641A - Three area vane type hydraulic pump having force modulating flow restrictor means - Google Patents

Three area vane type hydraulic pump having force modulating flow restrictor means Download PDF

Info

Publication number
US3401641A
US3401641A US527661A US52766166A US3401641A US 3401641 A US3401641 A US 3401641A US 527661 A US527661 A US 527661A US 52766166 A US52766166 A US 52766166A US 3401641 A US3401641 A US 3401641A
Authority
US
United States
Prior art keywords
pressure
vane
fluid
pump
chamber
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
US527661A
Other languages
English (en)
Inventor
Cecil E Adams
Randall E Griffith
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.)
American Brake Shoe Co
Original Assignee
American Brake Shoe Co
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 American Brake Shoe Co filed Critical American Brake Shoe Co
Priority to US527661A priority Critical patent/US3401641A/en
Priority to GB47912/66A priority patent/GB1168267A/en
Priority to AT1009566A priority patent/AT265028B/de
Priority to DE19671653801 priority patent/DE1653801A1/de
Priority to CH226667A priority patent/CH457148A/de
Application granted granted Critical
Publication of US3401641A publication Critical patent/US3401641A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • F01C21/0881—Construction of vanes or vane holders the vanes consisting of two or more parts
    • 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
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member

Definitions

  • ABSTRACT OF THE DISCLOSURE In a vane pump of the type which includes hydraulically operated pistons for vane control and wherein pressure to urge the pistons outwardly is applied to the pistons from a pressure zone through an interconnecting pressure chamber, flow restricting means are provided in the pressure chamber between each two adjacent piston cylinders, to reduce the pressure acting on the pistons as flow through the restrictors increases with pump speed. This automatically reduces the pressure force component on the pistons when the centrifugal force component is increased, so that the total force on the vanes at high operating speeds is modulated.
  • This invention is directed to improvements in hydraulic pumps of the vane type which include hydraulic means for vane control. More specifically, the invention relates to means for preventing damage to the vane tips and the cam ring such as is normally encountered due to increased total force acting outwardly on the vanes as the rotational speed of the pump increases.
  • a typical hydraulic pump of the vane type includes a rotor having a plurality of radially movable vanes carried in slots spaced around its periphery. These vanes engage the cam surface of a fixed stator or cam ring which surrounds the rotor. lnlet and outlet ports open at spaced positions into the area between the periphery of the rotor and the cam surface and are swept or traversed sequentially by the vanes as the rotor turns, whereby fluid received at the inlet port is transferred by the vanes to the outlet port.
  • the fluid pressures acting on two of the areas associated with each vane are substantially equal but act in opposite directions, and the forces resulting from these pressures thus tend to counteract each other.
  • the first area comprises a surface on the radially outer end of the vane and is subjected to pressure which urges the vane inwardly in its slot.
  • the second vane area comprises a surface on the radially inner end of the vane. The second area is subjected to a pressure equal but opposed to that acting on the first area, which pressure urges the vane outwardly in its slot.
  • a third area associated with each vane is also subjected to a fluid pressure which urges the vane outwardly. Pressure on this third area provides a controlling hydraulic force which, in addition to centrifugal force, urges the vane outwardly to eflect and maintain a fluid seal between the outer end of the vane or vane tip and the cam ring.
  • Three area pumps of the type to which this invention relates include a rotor :assembly having an internal 3,401,641 Patented Sept. 17, 1968 "ice pressure chamber and a pressure differential operated pin or piston associated with each vane, the piston being slidable in a bore intersecting the pressure chamber and leading radially to the vane. Fluid pressure in the chamber acts on the pistons and provides the third area force holding the vanes outwardly. Pressure is supplied into this chamber through passageways from a high pressure zone of the pump whenever the pressure in the chamber tends to drop sufficiently below the pressure in the high pressure zone.
  • the third area means may, for example, comprise a piston having an axial passage and an outer end which forms a check valve with the inner end of the respective vane for regulating the flow of pressure fluid from the pressure port into a pressure chamber interconnecting the inner ends of all the pistons.
  • the total force acting on a vane to force it outwardly in its slot has two components: a fluid pressure force component dependent on the output pressure of the pump, and a centrifugal force component arising from and dependent on the speed of operation of the pump. It has long been accepted as normal by those skilled in this art that the total outward force on the vanes of a pump increases as the speed of the pump increases.
  • This invention arises from our determination that, at constant pump output pressure, the total force urging the vanes outwardly against the cam ring at higher speeds should be lower than the total force urging the vanes out- Wardly at the minimum operating speed of the pump.
  • the total outward force acting on the vanes can be reduced or modulated by the use of fiow restrictors or orifices in the passage means for conducting hydraulic liquid to the third areas on the inner ends of the piston pins. These flow restrictors or orifices function to progressively reduce the hydraulic component of the total force acting to urge the vanes outwardly against the cam ring as the speed of the pump increases.
  • Another object of this invention has been to modulate by reducing the fluid pressure force component acting on the vanes as the speed of operation of the pump increases, i.e., to reduce the total outward force on the vanes as the speed of the pump increases, pump output pressure remaining constant, so that the total force, i.e., the sum of 3 the fluid pressure force and the centrifugal force on the vanes, decreases with pump speed.
  • FIGURE 1 is an axial section of a three-area type vane pump incorporating a preferred embodiment in accordance with the principles of this invention
  • FIGURE 2 is a partial transverse or radial section taken along line 2-2 of FIGURE 1;
  • FIGURE 3 is a perspective view depicting the sleeve structure of the preferred embodiment.
  • FIGURE 4 is an enlarged view of a portion of the sleeve, pressure chamber, rotor and pistons shown in FIGURE 2.
  • the three-area vane pump shown by way of illustration in the drawings includes a housing or casing formed by a body casting 1 having a generally cylindrical interior chamber, and an end cap 2 having a cylindrical boss 3 which telescopes into the end of the body and is sealed thereto by an O-ring 4.
  • the end Wall 5 of the body opposite end cap 2 includes a bore through which the pump operating shaft 6 extends. Shaft 6 is supported for rotation in this bore by a bearing (not shown) which is secured against axial movement in the bore. Shaft 6 extends from the body 1 into end cap 2 and is carried for rotation therein by a needle type roller bearing 7 mounted within a central bore in the end cap.
  • Cylindrical boss 3 of the end cap is finished to form a flat inner surface which is clamped against a side or radial face 8 of a cam ring 9. It may be mentioned here that the cam ring itself as well as the housing and cam ring together are sometimes referred to in the art as a stator.
  • a fluid intake passageway 10 extends radially into body 1 and communicates with a pair of internal annular channels 11, 12 which encircle the internal cavity within the body. These annular channels 11, 12 distribute fluid from the intake passageway 10 to suction ports to be described.
  • the cam ring 9 is supported radially by an annular rib 13 formed in the body 1 between the annular channels 11, 12.
  • the cam ring 9 encircles a rotor 14 which is connected to shaft 6 through a motion permitting spline joint 15 that perimts proper running alignment between the rotor, the fiat surface of the cylindrical boss 3, and a movable check plate 16.
  • Rotor 14 is provided with a plurality of radial vane slots 17 in each of which a vane 18 is mounted.
  • the cam ring 9 has a cam surface 19 that is contoured to provide a balanced or symmetrical pump construction in which there are diametrically opposite low pressure or suction zones 20, fluid transfer zones 21, high pressure or exhaust zones 22, and sealing zones 23 formed between the cam surface and the rotor 14 (see FIG. 2).
  • the cam surface 19 is formed in formed in part from a first pair of arcs of equal radii which extend across the fluid transfer zones 21 and, in part, by a second pair of arcs of shorter radii than the first pair of arcs which extends across the sealing zones 23. These pairs of arcs are interconnected by cam surfaces which extend across the low and high pressure zones and 22 respectively.
  • Cheek plate 16 is finished to provide a smooth flat radial surface on the inner side thereof which abuts the cam ring 9, and has a central bore 24 surrounded by a cylindrical boss 25 which extends into the bore in the wall 5 of the body 1 and is sealed thereto by an O-ring 26.
  • the outer cylindrical surface of cheek plate 16 is sealed to body 1 by an O-ring 27.
  • the cheek plate 16 is movable axially in the body 1 and is urged toward rotor 14 by fluid pressure supplied from the high pressure zone 22 through passageways 2S and 29 to a pressure chamber 30 formed between the body and the outer face 31 of the cheek plate.
  • the cheek plate functions in the nature of an axially movable, non-rotatable piston under the pressure supplied by the fluid in chamber 33 to maintain it in engagement with the adjacent side face of the cam ring'9.
  • Intake passageway 10 communicates through annular channels 11, 12 around the cam ring 9 to suction ports spaced 180 apart.
  • Two suction ports one of which is shown at 50 in FIG. 2, are formed in cheek plate 16 and are fed by channel 12, and two additional suction ports (not shown) are formed in end cap 2 and are fed by channel 11.
  • These suction ports in the end cap and cheek plate are identical in shape and are axially aligned with the suction zones 20 between rotor 14 and cam surface 19.
  • Each suction port has a branch passage, the opening of one of which is designated at 51, whereby the suction port communicates with the inner ends 32 of vane slots 17 in the rotor 14 as well as with the inlet zones 20.
  • the end cap 2 includes two diametrically opposed crescent-shaped exhaust or pressure ports 52, 52 which are spaced substantially 90 from the suction ports.
  • pressure ports 56, 56 are formed in cheek plate 16 which are axially aligned with the pressure zones 22 and with ports 52, 52 in the end cap.
  • Each pressure port 52 and 56 communicates with the inner ends 32 of the vane slots 17 in the rotor as the vane slots pass the ports through branch ports 54.
  • Pressure potrs 52, 52 are connected with a fluid outlet or delivery chamber 34 by a passageway 35 in the end cap 2.
  • cam surface 19 In the direction of rotor movement (clockwise as shown by the arrow in FIG. 2), the cam surface 19 progressively recedes from the periphery of the rotor 14 across the suction zones 20. In the transfer zones 21 cam surface 19 has a nearly constant radial spacing from the rotor, and across the exhaust zones 22 the cam surface progressively approaches the rotor 14 as it comes into close proximity with the periphery of the rotor 14 in the sealing zones 23. Fluid from the suction ports is drawn into the fluid transport pockets defined between the successive vanes as those pockets become larger when the vanes 18 move through the suction zones 20. The fluid is positively displaced from the pockets as the volume thereof diminishes when the vanes move through the pressure zones 22, to thereby effect a pumping action.
  • Each vane 18 is provided with grooves 36 which are formed in its outer edge and opposite side edges.
  • One or more channels or bores 37 are also provided in each vane which communicate between the outer groove 36 of the vane and the inner end 32 of the vane slot. The grooves 36 and channels 37 insure that the fluid pressure acting on the first area or outer end surface or tip of any given vane will be substantially balanced at all times by the pressure acting on the second area or inner end surface of that vane.
  • one or more radial bores or piston cylinders 38 is formed in the rotor 14, extending inwardly from the inner end 32 of each vane slot 17.
  • the bores 38 are interconnected at their inner ends with an annular pressure chamber 39 having fluid under pressure therein.
  • fluid can flow into and out of pressure chamber 39 only through radial bores 38.
  • the pressure chamber 39 communicates with the bores 38 through orifices or flow restrictors 46 having cross-sectional dimensions which are small relative to the diameter of the bores 38.
  • the pressure chamber 39 is constructed, in part, by defining in rotor 14 an annular groove 57 having the same cross-sectional dimensions as the flow restrictors 46.
  • the chambers 58 are formed in a sleeve 40, as best seen in FIG. 3. Thereafter the sleeve is fitted and sealed in an axial recess in rotor 14 with the chambers 58 intermediate the flow restrictors 46, thus forming the pressure chamber 39.
  • the pressure chamber 39 includes the flow restrictors 46, the chambers 58, and the groove 57.
  • a generally cylindrical pin or piston valve element 41 is received in each radial bore 38.
  • Each piston 41 includes an axial bore 42 and is slidable in its cylinder 38 with which it is closely fitted so that leakage of fluid along the external walls of the piston is negligible.
  • the outer end of each piston 41 is conically tapered as at 43 and forms a valve with the flat inner edge surface 44 of each vane 18.
  • the lower end surface of each piston is preferably chamfered, as at 47, and presents a surface with which the fluid pressure force within the chamber 39 may cooperate to force the piston outwardly against the inner edge surface 44 of each vane.
  • the admission of fluid to the radial bores 38 is regulated by the balance of forces between the fluid pressure force acting inwardly upon the conical taper 43, tending to open the valve, and the opposing force arising from the fluid pressure in chamber 39 and the centrifugal force, tending to close the valve.
  • the length of the piston 41 is such as to permit it to move into and out of engagement with the fiat inner edge surface 44 of the vane 18, regardless of the position of the vane in its slot.
  • valve 41, 44 at the outer end of the piston functions in the manner of a check valve.
  • fluid pressure at the inner end 32 of a vane slot acting upon the conical taper 43 of the piston 41 sufficiently exceeds the pressure in chamber 39, the piston is moved inwardly in its bore 38 and valve 41, 44 opens.
  • Pressure fluid in the inner end 32 of vane slot 17 flows inwardly through bore 42 toward chamber 39 and restores, maintains, or increases the fluid pressure in the pressure chamber as necessary to balance the fluid pressure acting to open the valve 41, 44.
  • This action occurs when the vane slot 17 traverses a pressure zone 22, for fluid pressure in the zone 22 is usually the highest in the pump and the pres sure in chamber 39 is somewhat lower.
  • flow into the chamber 39 through the bores 38 from the high pressure zones 22 occurs at a higher rate at higher speeds, and tends to cause a reduction of pressure in the chamber relative to pump outlet pressure.
  • the fluid flow rate into and out of the pressure chamber 39 through the flow restrictors 46 is lower, and, therefore, the pressure drop as the fluid passes through the flow restrictors 46 is lower.
  • the fluid pressure force component is relatively high with the centrifugal force component being low
  • the fluid force component is relatively low (due to the increased pressure drops caused by the flow restrictors) with the centrifugal force component being high, thereby providing a modulating or control effect on the total force.
  • This force modulation reduces vane tip and cam ring wear at high speed operation which would otherwise result from the greater force.
  • the chambers 58 may be omitted, and that the pressure chamber may wholly be formed by narrow groove 57 itself.
  • the pressure drop across such a relatively long thin orifice tends to vary rather widely with the viscosity of the hydraulic fluid, with the result that pump performance varies with temperature. For that reason we prefer the embodiment shown, which is less sensitive to fluid viscosity changes.
  • the invention can also be utilized in solid pin three area pumps of the type shown in Adams et al. Patent No. 2,832,293.
  • each vane having associated with it a pressure operated piston slidable in a bore in said rotor, the said piston being movable into abutting contact with said vane in said slot to urgesaid vane outwardly,
  • passage means interconnecting the inner ends of said pistons with one another for supplying fluid under pressure from a pump delivery chamber to the inner ends of said pistons in said bores, said fluid tending to urge the same outwardly,
  • said passage means including relatively restricted fixed area orifice means between each two adjacent bores, whereby the operating pressure at the pistons is reduced with respect to the pressure in the pump delivery chamber as the speed of the pump increases.
  • passage means comprises an annular internal chamber within said rotor intersecting each said bore, said orifice means being formed in said annular chamber between said bores as areas of relatively restricted cross sectional area.
  • annular chamber has two orifice means in series relation between each two adjacent bores, said two orifice means being spaced in said annular chamber between said two bores by an enlarged area within said annular chamber.
  • annular chamber is formed in part by said rotor and in part by a sleeve secured within a central shaft bore in said rotor, said sleeve being adapted to engage an operating shaft.
  • a rotor assembly for a hydraulic pump of the vane type comprising:
  • each piston being movable in a radial bore extending inwardly in the rotor from the vane slot
  • conduits for applying pressure fluid to all of said pistons tending to urge the same outwardly into contact with said vanes said conduit interconnecting said radial bores in series relation, said conduit entering said bores inwardly of the pistons therein,
  • a rotor assembly for a hydraulic fluid pressure energy translating device of the vane type comprising:
  • each piston being movable in a radial bore extending inwardly in the rotor from the vane slot
  • a generally circular conduit formed within said rotor for applying pressure fluid to all of said pistons tending to urge the same outwardly into contact with said vanes, said conduit interconnecting all said radial bores in the rotor inwardly of said pistons, said conduit restricting free fluid flow therethrough between said bores in operation,
  • each vane having associated with it a pressure operated piston means, the said piston means being arranged to urge said vane outwardly,
  • passage means for supplying fluid from a pump delivery chamber to each said piston means thereby tending to move said piston means and urge the vane outwardly in its slot
  • said passage means including pressure dropping orifice means through which fluid must flow to reach said piston means for reducing the operating pressure at the piston means with respect to the pressure in said delivery chamber as the rotational speed of the pump increases.
  • passage means comprises a chamber connected with each of said piston means, said pressure dropping orifice means being formed between said chamber and said piston means as a passage of relatively restricted cross-sectional area through which fluid must flow to reach said piston means.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
US527661A 1966-02-16 1966-02-16 Three area vane type hydraulic pump having force modulating flow restrictor means Expired - Lifetime US3401641A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US527661A US3401641A (en) 1966-02-16 1966-02-16 Three area vane type hydraulic pump having force modulating flow restrictor means
GB47912/66A GB1168267A (en) 1966-02-16 1966-10-25 Improvements in and relating to Vane-Type Pumps and Motors
AT1009566A AT265028B (de) 1966-02-16 1966-10-31 Flüssigkeitspumpe
DE19671653801 DE1653801A1 (de) 1966-02-16 1967-02-14 Kapselpumpe
CH226667A CH457148A (de) 1966-02-16 1967-02-15 Flügelradpumpe

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US527661A US3401641A (en) 1966-02-16 1966-02-16 Three area vane type hydraulic pump having force modulating flow restrictor means

Publications (1)

Publication Number Publication Date
US3401641A true US3401641A (en) 1968-09-17

Family

ID=24102400

Family Applications (1)

Application Number Title Priority Date Filing Date
US527661A Expired - Lifetime US3401641A (en) 1966-02-16 1966-02-16 Three area vane type hydraulic pump having force modulating flow restrictor means

Country Status (5)

Country Link
US (1) US3401641A (de)
AT (1) AT265028B (de)
CH (1) CH457148A (de)
DE (1) DE1653801A1 (de)
GB (1) GB1168267A (de)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3481276A (en) * 1967-11-27 1969-12-02 Abex Corp Vane tracking in hydraulic pumps
US3578888A (en) * 1969-04-18 1971-05-18 Abex Corp Fluid pump having internal rate of pressure gain limiting device
US4374632A (en) * 1981-02-02 1983-02-22 Abex Corporation Vane control for a vane motor
US4629406A (en) * 1984-02-10 1986-12-16 Atos Oleodinamica S.P.A. Volumetric vane pump for fluid-hydraulic drive
DE19703116A1 (de) * 1997-01-29 1998-07-30 Danfoss As Hydraulische Flügelzellenmaschine
US6663357B2 (en) * 2000-09-28 2003-12-16 Goodrich Pump And Engine Control Systems, Inc. Vane pump wear sensor for predicted failure mode
US20040131477A1 (en) * 2000-09-28 2004-07-08 Dalton William H. Vane pump wear sensor for predicted failure mode
WO2007140514A1 (en) * 2006-06-02 2007-12-13 Norman Ian Mathers Vane pump for pumping hydraulic fluid
US20090194382A1 (en) * 2005-11-04 2009-08-06 Helmut Ristl Clutch
US20110171054A1 (en) * 2009-06-25 2011-07-14 Patterson Albert W Rotary device
US20140147321A1 (en) * 2010-10-29 2014-05-29 Eaton Corporation Fluid device with pressurized roll pockets
US10788112B2 (en) 2015-01-19 2020-09-29 Mathers Hydraulics Technologies Pty Ltd Hydro-mechanical transmission with multiple modes of operation
US11085299B2 (en) 2015-12-21 2021-08-10 Mathers Hydraulics Technologies Pty Ltd Hydraulic machine with chamfered ring
US11168772B2 (en) 2009-11-20 2021-11-09 Mathers Hydraulics Technologies Pty Ltd Hydrostatic torque converter and torque amplifier
CN113915123A (zh) * 2021-10-25 2022-01-11 浙江威龙泵业有限公司 一种滑片泵
US11255193B2 (en) 2017-03-06 2022-02-22 Mathers Hydraulics Technologies Pty Ltd Hydraulic machine with stepped roller vane and fluid power system including hydraulic machine with starter motor capability
US20230304495A1 (en) * 2019-11-22 2023-09-28 Hanon Systems Efp Deutschland Gmbh Multiple-flow vane cell pump

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2809595A (en) * 1954-01-26 1957-10-15 American Brake Shoe Co Pump casing construction
US2968252A (en) * 1959-03-16 1961-01-17 New York Air Brake Co Engine
US3054357A (en) * 1958-08-07 1962-09-18 Daniel F Mcgill Dual pump power transmission
US3103893A (en) * 1960-06-30 1963-09-17 New York Air Brake Co Variable displacement engine
US3223044A (en) * 1963-07-18 1965-12-14 American Brake Shoe Co Three-area vane type fluid pressure energy translating devices
US3257958A (en) * 1965-03-29 1966-06-28 American Brake Shoe Co Rotary vane fluid power unit
US3329067A (en) * 1964-11-23 1967-07-04 Nils O Rosaen Fluid motors

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2809595A (en) * 1954-01-26 1957-10-15 American Brake Shoe Co Pump casing construction
US3054357A (en) * 1958-08-07 1962-09-18 Daniel F Mcgill Dual pump power transmission
US2968252A (en) * 1959-03-16 1961-01-17 New York Air Brake Co Engine
US3103893A (en) * 1960-06-30 1963-09-17 New York Air Brake Co Variable displacement engine
US3223044A (en) * 1963-07-18 1965-12-14 American Brake Shoe Co Three-area vane type fluid pressure energy translating devices
US3329067A (en) * 1964-11-23 1967-07-04 Nils O Rosaen Fluid motors
US3257958A (en) * 1965-03-29 1966-06-28 American Brake Shoe Co Rotary vane fluid power unit

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3481276A (en) * 1967-11-27 1969-12-02 Abex Corp Vane tracking in hydraulic pumps
US3578888A (en) * 1969-04-18 1971-05-18 Abex Corp Fluid pump having internal rate of pressure gain limiting device
US4374632A (en) * 1981-02-02 1983-02-22 Abex Corporation Vane control for a vane motor
US4629406A (en) * 1984-02-10 1986-12-16 Atos Oleodinamica S.P.A. Volumetric vane pump for fluid-hydraulic drive
DE19703116A1 (de) * 1997-01-29 1998-07-30 Danfoss As Hydraulische Flügelzellenmaschine
US6663357B2 (en) * 2000-09-28 2003-12-16 Goodrich Pump And Engine Control Systems, Inc. Vane pump wear sensor for predicted failure mode
US20040131477A1 (en) * 2000-09-28 2004-07-08 Dalton William H. Vane pump wear sensor for predicted failure mode
US7207785B2 (en) 2000-09-28 2007-04-24 Goodrich Pump & Engine Control Systems, Inc. Vane pump wear sensor for predicted failure mode
US20090194382A1 (en) * 2005-11-04 2009-08-06 Helmut Ristl Clutch
US20100028181A1 (en) * 2006-06-02 2010-02-04 Norman Ian Mathers Vane pump for pumping hydraulic fluid
WO2007140514A1 (en) * 2006-06-02 2007-12-13 Norman Ian Mathers Vane pump for pumping hydraulic fluid
CN101490420B (zh) * 2006-06-02 2011-07-27 诺曼·伊恩·马瑟斯 泵送液压流体的叶片泵
US8708679B2 (en) * 2006-06-02 2014-04-29 Mathers Hudraulics Pty. Ltd. Vane pump for pumping hydraulic fluid
US20110171054A1 (en) * 2009-06-25 2011-07-14 Patterson Albert W Rotary device
US8602757B2 (en) * 2009-06-25 2013-12-10 Albert W. Patterson Rotary device
US11168772B2 (en) 2009-11-20 2021-11-09 Mathers Hydraulics Technologies Pty Ltd Hydrostatic torque converter and torque amplifier
US9341063B2 (en) * 2010-10-29 2016-05-17 Eaton Corporation Fluid device with roll pockets alternatingly pressurized at different pressures
US20140147321A1 (en) * 2010-10-29 2014-05-29 Eaton Corporation Fluid device with pressurized roll pockets
US10788112B2 (en) 2015-01-19 2020-09-29 Mathers Hydraulics Technologies Pty Ltd Hydro-mechanical transmission with multiple modes of operation
US11085299B2 (en) 2015-12-21 2021-08-10 Mathers Hydraulics Technologies Pty Ltd Hydraulic machine with chamfered ring
US11255193B2 (en) 2017-03-06 2022-02-22 Mathers Hydraulics Technologies Pty Ltd Hydraulic machine with stepped roller vane and fluid power system including hydraulic machine with starter motor capability
US20230304495A1 (en) * 2019-11-22 2023-09-28 Hanon Systems Efp Deutschland Gmbh Multiple-flow vane cell pump
CN113915123A (zh) * 2021-10-25 2022-01-11 浙江威龙泵业有限公司 一种滑片泵

Also Published As

Publication number Publication date
DE1653801A1 (de) 1971-06-09
CH457148A (de) 1968-05-31
GB1168267A (en) 1969-10-22
AT265028B (de) 1968-09-25

Similar Documents

Publication Publication Date Title
US3401641A (en) Three area vane type hydraulic pump having force modulating flow restrictor means
US3223044A (en) Three-area vane type fluid pressure energy translating devices
US2255785A (en) Fluid pressure device
US3964844A (en) Vane pump
EP0363112A2 (de) Leistungsantriebselement
US2832293A (en) Vane pump
US3986439A (en) Piston and slipper arrangement for hydraulic pump or motor
US4431389A (en) Power transmission
GB992095A (en) Variable displacement pump
US3932073A (en) Screw rotor machine with spring and fluid biased balancing pistons
US5833438A (en) Variable displacement vane pump having cam seal with seal land
US4008002A (en) Vane pump with speed responsive check plate deflection
US3574493A (en) Vane-type pumps
US2962972A (en) Power transmission
US2878753A (en) Vane pump
US2820417A (en) Fluid pressure energy translating device
US5738500A (en) Variable displacement vane pump having low actuation friction cam seal
US3359914A (en) Method and apparatus for improving efficiency of vane pumps
US2955542A (en) Vane pump
US2426100A (en) Hydraulic pump or motor of the radial cylinder type
US2823615A (en) Pump with pressure loaded bushings
US4242068A (en) Vane pump with bypass for leakage of fluid when bottom of vane is connected to undervane suction port
US3481276A (en) Vane tracking in hydraulic pumps
US2739539A (en) Power transmission
US3468263A (en) Power transmission