US3451346A - Power transmission - Google Patents

Power transmission Download PDF

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Publication number
US3451346A
US3451346A US682905A US3451346DA US3451346A US 3451346 A US3451346 A US 3451346A US 682905 A US682905 A US 682905A US 3451346D A US3451346D A US 3451346DA US 3451346 A US3451346 A US 3451346A
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United States
Prior art keywords
vane
pressure
vanes
track
slot
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Expired - Lifetime
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US682905A
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English (en)
Inventor
Raymond B Pettibone
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Vickers Inc
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Sperry Rand Corp
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Assigned to SPERRY CORPORATION reassignment SPERRY CORPORATION CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: SPERRY RAND CORPORATION
Assigned to VICKERS, INCORPORATED reassignment VICKERS, INCORPORATED ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: SPERRY CORPORATION A DE CORP.
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Expired - Lifetime legal-status Critical Current

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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
    • F01C21/0818—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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/344—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F01C1/3446—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 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 group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B53/00—Internal-combustion aspects of rotary-piston or oscillating-piston engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2730/00—Internal-combustion engines with pistons rotating or oscillating with relation to the housing
    • F02B2730/01—Internal-combustion engines with pistons rotating or oscillating with relation to the housing with one or more pistons in the form of a disk or rotor rotating with relation to the housing; with annular working chamber
    • F02B2730/012—Internal-combustion engines with pistons rotating or oscillating with relation to the housing with one or more pistons in the form of a disk or rotor rotating with relation to the housing; with annular working chamber with vanes sliding in the piston
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • a rotary fluid pressure energy translating device having a vane cam track within which is rotatably mounted a rotor carrying radially sliding vanes to form iluid inlet and Huid outlet working zones located between the periphery of the rotor and the vane track, the vanes being of the type having a thrust member telescopically disposed within each vane and forming an expansible pressure chamber therein, a surface of which is effective under pressure to urge the vane into engagement with the cam track, each vane having a balancing cavity on the face thereof, intersecting and in iluid communication with the said expansible pressure chamber, and a pressure porting arrangement for transmitting fluid under pressure to said expansible pressure chamber.
  • This invention relates to power transmissions, and is particularly applicable to those of the type comprising two or more uid pressure energy translating devices, one of which may function as a pump, and the other as a fluid motor. More particularly, this invention relates to an improvement in sliding vane type pumps and motors such as illustrated in the patent to Duncan B. Gardiner, No. 2,967,488.
  • Units of this type generally comprise a stator including a vane cam track within which is rotatably mounted a rotor carrying radially sliding vanes to form iluid inlet and uid outlet working zones located between the periphery of the rotor and the vane track, either of which may be a low or a high pressure working zone dependent upon the pump or motor function of the device.
  • the vanes as followers are adapted to follow the cam track and to provide proper sealing between inlet and outlet porting corelated with the iluid inlet and fluid outlet zones.
  • the vanes are urged outwardly and into engagement with the track by centrifugal force and also by providing a controlled pressure unbalanced condition between an outer track engaging surface and an inner and an intermediate surface of the vane.
  • the vane is urged inwardly by mechanical cam action of the track.
  • the level of leakage between the inner, intermediate, and outer surfaces of the vane is kept within acceptable limits to assure the pressure unbalanced condition by providing a relatively small clearance space between the vane and the walls of the coresponding rotor slots.
  • the adverse condition are minimized by providing enlarged feed passages in the rotor slot walls on opposite Sides of each vane, thus, a means is established for providing pressure fluid to the opposite interface surfaces of each vane and to the intermediate surface therein ⁇ and the resultant opposing hydraulic forces between the vane and slot wall interface tends to laterally stabilize the vane.
  • the leakage between the inner, intermediate, and outer surfaces of the vane exceeds the herebefore mentioned ⁇ acceptable limits necessary to assure a proper pressure unbalanced condition for maintaining the vane in engagement with the track.
  • Elimination of one of the enlarged feed passages was found to bring the aforementioned leakage to within acceptable limits, however, scoring and vane seizure occurred. This problem is believed to have resulted from lack of lateral stabilization of the vanes.
  • This invention eliminates the scoring and seizure problems while maintaining very low leakage levels.
  • This invention comprises a rotary fluid energy translating device of the sliding vane type with a rotor having radial slots with a plurality of pressure chambers associated therewith, a balancing cavity in fluid communication with one of said pressure chambers for preventing contact between the vane and corresponding slot wall.
  • FIG. l is a longitudinal, sectional view of a device embodying the present invention and taken on line 1--1 of FIG. 2.
  • FIG. 2 is a sectional view taken on line 2-2 of FIG. 1.
  • FIG. 3 is an enlarged partial sectional view of the vanes and porting arrangement associated therewith shown in FIG. 2.
  • FIG. 4 is a partial sectional view taken on line 4-4 of FIG. 3.
  • FIG. 1 there is shown a rotary, sliding vane device or pump, indicated generally by the numeral 10, the housing of which comprises a vane cam track section 12 sandwiched between a body member 14 and an end cover 16, all of which are secured to each other by bolts 18 extending through cover 16 and cam section 12 into threaded holes in body 14.
  • the body section 14 is provided with an inlet supply connection port 20 having an inlet passage 22 leading therefrom which has two branches 24 and 26 respectively terminating in a pair of fluid port openings 28 and 30 which are shown in hidden lines in FIG. 2.
  • An outlet connection port 32 is provided in the end cover 16 which is directly connected to a pressure delivery chamber 34 formed in an enlarged bore 36 of the end cover 16 where a pressure plate 38 is fioatably mounted in the bore 36.
  • the pressure plate 38 is urged rightwardly by outlet pressure in the chamber 34 so that the outer portion of a plane side surface thereof and indicated by the numeral 40, is maintained in engagement with the immediately adjoining surface of a rotor 42 and vanes carried thereby within the cam section 12.
  • Spring 43 initially biases the pressure plate 38 toward the rotor until pressure builds up in the pressure chamber.
  • the rotor 42 is rotatably mounted within cam section 12 on the splined end 44 of shaft 46 which is rotatably mounted within bearings 48 and 50 mounted within the body section 14.
  • the shaft 46 is provided with a seal 52 while O ring seals 53 and 54 prevents leakage at the juncture of the cam ring section 12 with the body 14 and end cover 16.
  • the contour of the inner surface of the cam section 12 forms a vane track substantially elliptical in shape indicated by the numeral 56 which together with the periphery of the rotor and the adjoining surfaces of the body and pressure plate dene two opposed working chambers indicated by the numerals 58 and 60, each of which, for the purposes of convenience, may be divided into fluid inlet and uid outlet zones and which forms a sliding vane device of the double throw type.
  • the fluid inlet zones comprise those portions of the working chambers 58 and 60 respectively registering with the fluid inlet port openings 28 and 30 of the inlet passages 24 and 26.
  • the fluid delivery zones comprise those portions of the working chambers 58 and 60 registering respectively with opposed arcuately shaped uid delivery port openings 62 and 64 (shown in dot-dash lines in FIG. 2 to indicate positional relationship) which are recessed in the surface 40 of the pressure plate 38 and which are directly connected to the pressure chamber 34 by means of duplicate passages 66 leading therefrom, one of which is shown in FIG. l.
  • the vane track of the device includes an inlet zone ramp extending from a to b, a true arc portion extending from b to c, a delivery zone ramp extending from c to d and another true arc portion extending from d to e.
  • the track is symmetrical about each of its major and minor axes, thus each of the ramp and true arc portions from a to e are duplicated in the remaining opposed portions of the track.
  • the radial slots 70 in the rotor are formed by the parallel walls which guide the vanes as they move radially inward and outward and are indicated by the numbers 71 and 72 (FIG, 3) and also the enlarged pressure chamber at the inner end of each slot and indicated by the numeral 73.
  • the spacing between each pair of vanes is adapted to span the distance between each pair of ports in a manner to provide proper sealing between the inlet and outlet porting connected to the working chambers of the device.
  • a plurality of angular passages 74 is provided, one for each slot, which lead from the periphery of the rotor to the inner enlarged chambers 73 0f the vane slots.
  • the passages 74 are adapted to transmit to the vane slot pressure chambers 73 and thus to the inner surfaces of 75 the vanes indicated by the numeral 75, the cyclically changing pressure which is exerted on the outer edges 76 of the vanes 68 as they traverse the inlet and outlet ramps of the vane track.
  • a reaction member for each vane, indicated by the numeral 78, which together with a correlated porting arrangement provides a controlled unbalance on the suction stroke or inlet phase of the device which insures complete extension of the vanes and also maintenance of the outer edges of the vanes in contact with the vane track through the complete rotary cycle of the device.
  • the vanes 68 of the present invention device differ from the flat sided substantially rectangular vanes of the conventional devices by having two rectangular milled out sections, one of which extends from the inner end of the vane to substantially the mid-section thereof, which is indicated by the numeral 80, and the side walls of which are indicated by the numeral 82.
  • the second rectangular milled out section comprises a balancing cavity 84 later described.
  • the aforementioned reaction member 78 comprises a fiat sided blade substantially equal in width and thickness to that of the milled out section 80 of the vane so as to have a sliding telescoping fit within the side walls 82 of the vane and the side walls 71 and 72 of each vane slot.
  • Each vane 68 also includes an oval shaped expansible pressure chamber 86 defined by the side walls of the vane slot and the extended cutaway portion of the vane and in which is exposed a pressure responsive outer end surface 88 of the reaction member 78.
  • the inner end 90 of each reaction member 78 extends from the inner end of the vane into the pressure chamber 73 of the vane slot.
  • the second of the aforementioned milled out sections, balancing cavity 84 extends across a face 91 of the vane 68 at substantially the mid-section thereof in an axial direction and is in communication with the expansible pres
  • the balancing cavity will operate most effectively when it has a shallow depth. By limiting the depth of the cavity, there is created a restricted flow path across the cavity, thus the level of leakage losses may be maintained at an acceptable level, while a pressure field, which is sufiicient to laterally stabilize the vane, may be maintained between the vane and slot wall surfaces.
  • the depth indicated by the numeral 92 in FIG. 3, has been exaggerated for purposes of illustration.
  • Pressure in the pressure chamber 86 also acts against the outer exposed surface of said chambers to urge the reaction members 78 to the position recited, wherein the tapered inner end thereof is bottomed against an inner surface 93 of the vane slot pressure chamber 73.
  • a pressure responsive surface opposing the pressure responsive surface 88 of the reaction members 78 is formed on each vane, indicated by the numeral 94, comprising a portion of the upper surface, as viewed in FIG. 4, of the reaction pressure chamber 86.
  • the effective area of the surface 94 is equal to the projected area of the pressure responsive surface 88 of the reaction member 78.
  • the pressure plate 38 is provided with a plurality of passages 9S, one of which is shown in FIG. 1, lwhich extends from the pressure chamber side of the plate through said plate to a circular pressure groove 96 recessed in the plane surface 40 of the plate immediately adjacent the rotor.
  • a mirror image 98 of this pressure groove may be constructed in a plane surface 100 of the body section 14 on the opposite side of the rotor.
  • the pressure grooves 96 and 98 register with the opposite ends of a plurality of half-round holes 102 arranged in circular formation in the rotor.
  • the holes 102 extend completely through the rotor on each wall 72 of the slots 70 while also communicating with the reaction member pressure chamber 86 at the face 104 of the vanes 68.
  • fluid is conducted to the inlet port openings 28 and 30 adjacent the inlet ramp portion -of the vane track by means of passage 22 and branch passages 24 and 26.
  • fluid is Withdrawn through the inlet port openings 28 and 30 into the intervane spaces and carried to the outlet ports 62 and 64 from where it is discharged through the outlet port 32 by the medium of the pressure plate outlet ports 62 and 64, the pressure plate outlet passages 66, and the pressure chamber 34 which is directly connected to the outlet port 32.
  • a controlled vane pressure unbalance for aiding centrifugal force in rapidly and completely extending the vanes and maintaining the outer edges thereof in engagement with the vane track is provided by the transmission of pressure from the pressure chamber on the outlet side of the device to the reaction member pressure chambers 86, through the medium of pressure plate passages 94 and groove 96 and the rotor passages i102.
  • the outer surfaces 88 of the reaction members are exposed to the pressure within the chambers 86 and the reaction members 78 are urged to a bottoming position with their inner ends 90 engaging the inner surfaces 93 of the vane slot pressure chambers 73.
  • the pressure transmitted to the pressure chamber 86 is transmitted equally tothe balancing cavity 84 and while the vane moves inwardly and outwardly, a hydrodynamic film is established between the vane face 91 and the slot wall 71 which will tend to laterally stabilize the same while providing a lubricating medium for preventing metal to metal contact between the vane and slot wall. Further, any debris or other contaminants from the vane-rotor slot interface areas which may be trapped therein will be flushed out through the balancing cavity which otherwise would promote scoring of the vane faces, and slot walls or possible vane seizure and ultimately prevent the vane from properly maintaining contact with the vane track 56.
  • connection of the outlet side of the device to the reaction member pressure chambers produces a resultant outward force on the vane which not only aids centrifugal force in completely extending the same, but produces a continuous, controlled force in favor of maintaining the outer edges 76 of the vane 68 in contact with the vane track 56 and connection of the outlet side of the device also to the balancing cavity 84, produces a balanced condition between the vane and slot wall which allows the vane to move radially inward and outward with a minimum amount of friction.
  • the balancing cavity 84 is located on the vane face 91 and produces a hydraulic lforce which tends to separate the vane from the slot wall 71.
  • the hole 102 is located on the slot wall 7,2 and produces a hydraulic force which. tends to separate the vane from it.
  • the size of each balancing cavity and hole relative to the vanes is preselected in order that the total resultant force balance between the vanes and the slot walls will be such as to laterally stabilize the vane to prevent contact between the walls and vanes so as to insure rapid, complete movement of the vanes.
  • the resultant inward and outward forces on the vanes are substantially balanced.
  • the pressure existent in the outlet working zones of the device and imposed on the outer edges 76 of the vanes 68 is transmitted to the innermost areas 7S of the vanes through the medium of the passages 74.
  • Pressure is conducted to the surface 94 and groove 96 an dthe rotor passages 102.
  • the vanes are thus substantially balanced during the discharge phase of the device.
  • each vane will function in the same manner when the vanes pass through the outlet working zones of the device, as the herebefore described operation when the vanes pass through the inlet Zones of the working chambers of the device.
  • the present invention has provided a rotary fluid pressure energy translating device wherein a controlled pressure balance between each vane and corresponding slot walls is provided for laterally stabilizing the vane, thus preventing metal to metal contact between the vane and rotor slot walls, while providing a limited amount of leakage between 'the inner, intermediate and outer surfaces of the vane, thus, assuring an extension 'of the vanes for engagement with the track.
  • Devices embodying the invention operate at much higher pressures and speeds than conventional devices of the type herebefore used, yet minimize excessive rwear while providing utmost efliciency and long life.
  • a rotary fluid energy translating device of the sliding vane type including low and high pressure operating passages, one of which is an inlet passage and the other an outlet passage, and a vane track; a rotor having a plurality of radial slots, each slot being defined by two parallel side surfaces, and rotatably within the track; a vane slidable in each slot having parallel side surfaces guided by said corresponding slot surfaces, a track engaging outer end surface, an intermediate surface and an inner end surface, both of said latter two surfaces being effective under pressure for urging the vane outer surface toward the track; a reaction member including an outer end surface radially disposed within each vane for telescopic movement relative thereto and forming an expansible chamber, two directly opposed walls of which are the intermediate vane surface and associated reaction member outer end surface; passage means connecting the high pressure operating passages ⁇ of the device to said expansible chamber; that improvement which comprises means forming a shallow balancing cavity in one of said vane surfaces on each vane and facing one of said corresponding slot surfaces; and
  • passage means connecting the high pressure operating passages of the device to said eXpansible chamber includes a recess formed in each of said slots on the side surface opposite the said one corresponding slot surface, said recess being in fluid communication with said expansible chamber.
  • a rotary fluid energy translating device of the sliding vane type including low and high pressure operating passages, one of which is an inlet passage and the other an outlet pasage, and a vane track; a rotor having a plurality of radial slots, each slot being defined by two parallel side surfaces, and rotatable within the track; a vane slidable in each slot having parallel side surfaces guided by said corresponding slot surfaces, a track engaging outer end surface upon which cyclically changing pressure is irnposed, and also having an intermediate surface and an inner end surface, both of said latter two surfaces being effective under pressure for urging the vane outer surface toward the track; a reaction member including an outer end surface radially disposed Within each vane for telescopic movement relative thereto and forming an expansible chamber, two directly opposed walls of which are the intermediate vane surface and associated reaction member outer end surface, means forming a second eXpansible chamber in communication with the inner surfaces of the vanes, first passages means for conducting the cyclically changing pressure to
  • said first passage means includes a recess formed in each of said slots 8 on the surface 'opposite the said one corresponding slot surface, said recess being connected to said first expansible chamber; said second passage means is connected to said second expansible chamber; ⁇ and said balancing cavity means being connected to said first expansible chamber.
  • a rotary fiuid energy translating device of the sliding vane type including lozw and high pressure operating passages, one of which is an inlet passage and the other an outlet passage, and a vane track; a rotor having a plurality of radial slots, each slot being defined by two parallel side surfaces, a Vane slidable in each slot having parallel side surfaces guided by said corresponding slot surfaces, a track engaging outer end surface upon which cyclically changing pressure is imposed; means forming separate surfaces associated with each vane, said surfaces being effective under pressure to urge the vanes towards the track; means forming separate pressure chambers in each slot one of which is associated with one of said separate surfaces, the other associated with the other of said separate surfaces; a first passage means for conducting the cyclically changing pressure to one of said expansible chambers, and a second passage means for conducting the high pressure passage to the other of said expansible chambers; that improvement which comprises means forming a shallow balancing cavity in one of said vane parallel side surfaces on each vane and facing one of said said van

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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)
  • Hydraulic Motors (AREA)
US682905A 1967-11-14 1967-11-14 Power transmission Expired - Lifetime US3451346A (en)

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US68290567A 1967-11-14 1967-11-14

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US682905A Expired - Lifetime US3451346A (en) 1967-11-14 1967-11-14 Power transmission

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DE (1) DE1808826A1 (enrdf_load_stackoverflow)
GB (1) GB1251816A (enrdf_load_stackoverflow)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3514237A (en) * 1968-07-25 1970-05-26 Ingersoll Rand Co Fluid motion device
US3535062A (en) * 1967-09-21 1970-10-20 Towler Hydraulics Ltd Vane pumps
US3813194A (en) * 1971-11-20 1974-05-28 Rexroth Gmbh G L Hydraulic vane machine with controlled vanes
US4431389A (en) * 1981-06-22 1984-02-14 Vickers, Incorporated Power transmission
US5733109A (en) * 1995-07-12 1998-03-31 Coltec Industries Inc. Variable displacement vane pump with regulated vane loading
JP3437568B2 (ja) 1988-10-05 2003-08-18 ヴィッカーズ，インコーポレイテッド 圧力伝達装置
US20060133946A1 (en) * 2003-07-15 2006-06-22 Mathers Norman I Hydraulic machine
US20090280021A1 (en) * 2003-07-15 2009-11-12 Norman Ian Mathers Hydraulic machine
US20110176909A1 (en) * 2010-01-21 2011-07-21 Showa Corporation Vehicle hydraulic control unit
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
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

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2967488A (en) * 1957-02-07 1961-01-10 Vickers Inc Power transmission
US2967489A (en) * 1957-02-07 1961-01-10 Vickers Inc Power transmission
US3014431A (en) * 1958-08-15 1961-12-26 Shell Oil Co Sliding vane pump
US3187678A (en) * 1959-05-19 1965-06-08 Sperry Rand Corp Power transmission
US3230840A (en) * 1963-05-22 1966-01-25 Elliott F Hanson Fluid operated device
US3238885A (en) * 1964-02-10 1966-03-08 Ford Motor Co Positive displacement fluid pump
US3254606A (en) * 1963-12-16 1966-06-07 Nils O Rosaen Constant delivery pump
US3291384A (en) * 1965-09-15 1966-12-13 Frisk Company Rotary compressor

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2967488A (en) * 1957-02-07 1961-01-10 Vickers Inc Power transmission
US2967489A (en) * 1957-02-07 1961-01-10 Vickers Inc Power transmission
US3014431A (en) * 1958-08-15 1961-12-26 Shell Oil Co Sliding vane pump
US3187678A (en) * 1959-05-19 1965-06-08 Sperry Rand Corp Power transmission
US3230840A (en) * 1963-05-22 1966-01-25 Elliott F Hanson Fluid operated device
US3254606A (en) * 1963-12-16 1966-06-07 Nils O Rosaen Constant delivery pump
US3238885A (en) * 1964-02-10 1966-03-08 Ford Motor Co Positive displacement fluid pump
US3291384A (en) * 1965-09-15 1966-12-13 Frisk Company Rotary compressor

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3535062A (en) * 1967-09-21 1970-10-20 Towler Hydraulics Ltd Vane pumps
US3514237A (en) * 1968-07-25 1970-05-26 Ingersoll Rand Co Fluid motion device
US3813194A (en) * 1971-11-20 1974-05-28 Rexroth Gmbh G L Hydraulic vane machine with controlled vanes
US4431389A (en) * 1981-06-22 1984-02-14 Vickers, Incorporated Power transmission
JP3437568B2 (ja) 1988-10-05 2003-08-18 ヴィッカーズ，インコーポレイテッド 圧力伝達装置
US5733109A (en) * 1995-07-12 1998-03-31 Coltec Industries Inc. Variable displacement vane pump with regulated vane loading
US20060133946A1 (en) * 2003-07-15 2006-06-22 Mathers Norman I Hydraulic machine
US20090280021A1 (en) * 2003-07-15 2009-11-12 Norman Ian Mathers Hydraulic machine
US8597002B2 (en) 2003-07-15 2013-12-03 Mathers Hydraulics Pty. Ltd. Hydraulic machine with vane retaining mechanism
US9638188B2 (en) 2003-07-15 2017-05-02 Mathers Hydraulics Technologies Pty Ltd Hydraulic machine with vane retaining mechanism
US11168772B2 (en) 2009-11-20 2021-11-09 Mathers Hydraulics Technologies Pty Ltd Hydrostatic torque converter and torque amplifier
US20110176909A1 (en) * 2010-01-21 2011-07-21 Showa Corporation Vehicle hydraulic control unit
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

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Publication number Publication date
GB1251816A (enrdf_load_stackoverflow) 1971-11-03
DE1808826A1 (de) 1969-08-07

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