US3404632A - Rotary volumetric pump - Google Patents

Rotary volumetric pump Download PDF

Info

Publication number
US3404632A
US3404632A US524418A US52441866A US3404632A US 3404632 A US3404632 A US 3404632A US 524418 A US524418 A US 524418A US 52441866 A US52441866 A US 52441866A US 3404632 A US3404632 A US 3404632A
Authority
US
United States
Prior art keywords
pump
rotor
cam
cams
members
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
US524418A
Other languages
English (en)
Inventor
Reminiac Bernard
Tournel Marcel
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.)
RENOU DARDEL
Original Assignee
RENOU DARDEL
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 RENOU DARDEL filed Critical RENOU DARDEL
Application granted granted Critical
Publication of US3404632A publication Critical patent/US3404632A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • F04C2/356—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 outer member
    • F04C2/3568—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 outer member with axially movable vanes
    • 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
    • F01C1/356—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 outer member
    • F01C1/3568—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 outer member with axially movable vanes
    • 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
    • F03C2/00—Rotary-piston engines
    • F03C2/30—Rotary-piston engines having the characteristics covered by two or more of groups F03C2/02, F03C2/08, F03C2/22, F03C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • 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
    • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C2/063—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them
    • 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
    • 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
    • F04C2/3448—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 with axially movable vanes

Definitions

  • the object of the present invention is to provide a constamt-capacity rotary volumetric pump which can also be employed as a hydraulic motor, said pump having a single rotor, at least one of the axial ends of which constitutes an annular cam which denes one or a plurality of pump chambers through which sweeps at least one valve or closing member which is axially slidably mounted in the pump body and urged against the cam'.
  • the cam or each cam has alternately crests and hollows which are interconnected by portions of helical appearance over which the slidable valve member or each slidable valve member sweeps so that the liquid which enters a pump chamber through a port in the body located on one side of the valve member is discharged under the elect of the sweeping through a port in the body located on the other side of the valve member.
  • the even nature of the flow is a result already obtained in ai known rotary pump employing valve members slidably mounted in the pump body.
  • the valve members are radial and cooperateV with radial cams formed at the periphery of at least two rotors.
  • the pump according to the invention consequently has the advantage of a simplified construction owing to its single rotor and the possibility of obtaining direct from the foundry the iluid conduits in the stator, which is also a'single stator, with the result that drilling operations are restricted to the drilling of the lixing and drainage apertures.
  • the pump according to the invention is also advantageous in that it is easy to assemble. As the rotating part is in one piece no angular positioning of this part is necessary. As concerns the relative axial positioning of the rotoriand the parts of the pump body disposed in axially adjacent relation at both ends of the stator, Athe required position vand the ⁇ operational clearance can be obtained by adequately dimensioning the stator, this stator being therefore the sole part of the pump whose thickness must be strictly calibrated whereas in pumps having multiple radial rotors several precise axial dimensions are required between the spacer rings and correspondingrotors,
  • each end' of the rotor have a cam of identical contour, the two cams, which cooperate with the valve members disposed in an identical manner, being angularlyotset in such manner that the projection of their contour onto the outer cylindrical face of the rotor describes two parallel curves defining segments of a generatrix of equal length.
  • FIG. 1 is a perspective View of a pump according t the invention in which various eut-away portions show the construction of the stator and rotor;
  • FIG. 2 is an axial sectional view taken along line 2 2 of FIG. 3;
  • FIGS. 3 and 4 are sectional views taken along lines 3 and 4 4 respectively of FIG. 2;
  • FIG. 5 is an axial sectional view in plan of the pump, the upper portion of the stator having been removed;
  • FIG. 6 is an end elevational view of the driving shaft end of the pump showing the manner of securing the Pump;
  • FIG. 7 is a sectional view taken along line 7 7 of FIG. 2;
  • FIG. 8 is a sectional view taken along line 8 8 of FIG. 3;
  • FIG. 9 is a perspective view of the pump rotor
  • FIG. 10 is a diagrammatic view showing the dynamic balancing of the pump
  • FIG. 11 is a diagram indicating the flow curve of one pump chamber
  • FIG. 12 is a diagram showing a particular relative position ofthe cam and spacer plates
  • FIG. 13 is a diagram showing in superimposed relation the flow curves of individual chambers
  • FIG. 14 is a diagram showing the development of the profile of a part of a cam.
  • FIG. 15 shows the curve of the velocities of a valve member cooperating with the cam shown in FIG. 14.
  • the pump illustrated in the drawing comprises, within a body 1 of generally cylindrical shape, a single rotor 2 driven by a shaft 3.
  • the body-disposed at each end of a stator 4 in the bore 4a of which the rotor 2 is engaged includes two plates 6, 7 constituting spacer members which are positioned with respect to the stator by centering dowels 84 (FIG. 5), and end members 8, 9 which extend inwardly and constitute sleeves 10, 11, the assembly being held together by screws 5.
  • the shaft 3 is journalled inside the sleeve 10 of the member 8 by a needle rolling bearing 12 and in a counterbore 13 of the member 9 by a hall rolling bearing 14. Applied against the latter is a flange 15 of the shaft 3, this bearing being retained by a retainer ring 16 and a tlanged collar 17 which is held in position by a ring 18 (FIG. 2).
  • the collar 17 also acts as sealing means owing to the provision of a flexible ring 19 inserted in a recess in the outer periphery of the collar and. an annular membrane 22 which is located inside the collar backed by the ange 17a and slidably applied against the shaft.
  • the rotor 2 is prevented from rotating on the shaft 3 by a key 23 (FIG. 3) and is axially located by the lateral faces of the spacer plates 6, 7 which are sealed relative to the adjacent faces of the body 1 by rings 28.
  • the precise axial position of these lateral faces, on which depends the operational clearance for the rotor 2, is obtained by calibrating the thickness of the stator 4.
  • the fluid to be pumped enters by way of an aperture 34 provided in one of the vertical faces of the stator 4, flows into a part-circular conduit 36 (FIGS. 2 and 3) and is distributed in two diametrically opposed axial manifolds 37 the ends of which communicate with conduits 38 which are formed in the plates 6 and 7 and supply the pump chambers.
  • a part-circular conduit 36 As concerns the delivery or discharge, it is effected by an assembly comprising conduits 48, manifolds 47, a part-circular conduit 46, and a discharge aperture 44 which correspond respectively to the elements 38, 37, 36, 34 of the inlet system.
  • Rings 81 provide a seal lbetween the manifolds 37 and the conduits 38 and between the manifolds 47 and the conduits 48.
  • the discharge aperture is provided at a point on the stator diametrically opposed to the point at which the iiuid is admitted.
  • the pumping is effected by two radial faces constituting annular cams S1, 52 formed on the axial ends of the rotor 2 and each cooperating with two diametrically opposed closing or valve members 53, 54 which slide axially in the spacer plate 6 or 7 in contact with the wall of the bore 4a of the stator 4.
  • Each pair of valve members 53, 54 is biased against the corresponding cam by an annular spring 56 which is mounted to oscillate about an axis perpendicular to the line intersecting the valve members 53, 54 by means of two diametrically opposed studs 83 in the side member 8 or 9 and two V-shaped recesses 56a in the spring 56, the bottom of each recess bearing against the chamfered end 83a and the correslwnding stud 83.
  • the cam-contacting end of the valve members 53, 54 has preferably a semi-cylindrical shape.
  • the profiles of the two cams 51, 52 are identical'and consist' of six arcs of a helix a, b of equal length, the pitch of which is the same but changes sign from one arc to the following, these arcs being interconnected by six flat portions c or d spaced 60 apart, which gives a developed curve (FIG. 14) resembling a sinusoid having lattened crests c and hollows d.
  • the fiat portions c and d thus define two radial planes which are axially spaced apart a distance e.
  • each flat portion c or d is connected to the adjacent arc of a helix a or b by a suitable curved portion f (FIG. 14).
  • the profiles of the two cams 51, 52 are angularly offset 60 from each other so that the two profiles form two parallel faces.
  • these faces can be machined simultaneously by a single tool carrier supporting two radial tools spaced apart a distance I corresponding to the generatrices defined on the cylindrical outer face of the rotor by the intersection therewith of the cam profiles.
  • four grooves 61 are provided in the outer periphery of the rotor in contact with the bore 4a of the stator.
  • two groups of two grooves 67 are provided on the inner periphery of the rotor in contact with the sleeves and A11.
  • the leakage flow on the outer periphery of the rotor is automatically conducted to the suction pump chambers.
  • the leakage flow on the inner periphery of the rotor is drained towards the part-circular suction conduit 36. Connected to the latter through conduits 37, 38 (FIG.
  • annular springs undergo no stress variations, since they are pre-stressed on'assembly and rock on the studs 83 and therefore do not bend, owing to the alternating movement of the diametrically disposed valve members 53 and 54.
  • the ow remains zero between the positions and 180 of the crest c1, a new supply of fluid to the chamber w1 having started in front of the valve member 54 for the angular position 20 and terminating in the position 140.
  • a discharge cycle identical to the preceding cycle once again starts for the chamber w1 by utilization of the upper discharge conduit 48 located in front of the valve member 53.
  • FIGURE y13 shows the juxtaposition of six flow curves of "respective chamberswhich are identical toAtlie curve shown in FIGURE l1 -butoffset fromweachother in accordance-with an arrangement providing a? constant instantaneous-discharge or-delivery ofthe pump, namely a nonipulsatory discharge.
  • the flow in respect of a cam of the rotor is equal to the value of the maximum flow of a pump chamber, that is, either a single chamber discharges in the ⁇ zone of thek apexofmits curve or the flows of two chambers ⁇ complement each other so as to give this constant value.
  • FIGURE The diagram shown in FIGURE is intended to show that the axial thrusts due to pumping pressures exerted on the rotor are always balanced.
  • the referances m, n and m', n' represent the crests of the left and right cams respectively which define the rear limits of the chambers in which the discharge is in course.
  • FIGURE is a diagram of the linear velocity of a sliding valve member. It is clear that the velocity is constant in the passage of the valve member in the region of the helicalarcs a or b but that the velocity changes direction in the region of the crests and hollows of the adjacent cam.
  • the pump according to the invention can be constructed with a single cam on the rotor, the axiall thrust then exerted on the rotor ybeing compensated by a reaction device or thrust bearing employing mechanical or hydraulic means.
  • a pump according to the invention having two cams and ensuring the balancing of the axial forces could be provided with a hydraulic compensating device on one side oronboth sides of the rotor for automatically taking up clearances or play thereby resulting in performances which are unaffected by Wear of the component parts and consequently strictly constant over a' period of time.
  • the pump according to the invention could comprise in the region of each cam, or of the single cam, of the rotor a different number of pump chambers cooperating with a different number of sliding valve members.
  • Rotary displacement pump also of utility as a fluid motor, said pump comprising a yfixed part and a rotating part, said fixed part comprising a pump body having an axis, said rotating part consisting of a single rotor mounted in said body to rotate about said axis and means for driving said rotor in rotation, said rotor having at each end thereof an annular face cam, said body having inner annular end faces respectively cooperative with said cams, each cam having a progressively varying profile defining recess portions and crests, said crests being in sliding contact with said annular end faces whereby said recess portions of each cam define with said body a plurality of pump chambers which rotate with said rotor, closing members mounted in said body to slide in a direction substantially parallel to said axis and cooperative with said cams,4 elastically yieldable means biasing said closing members against said cams, whereby upon rotation of said rotor, saidclosing members sweep through said rotating pump chambers, and inlet ports and discharge ports provided in said body in positions to
  • Rotary displacement pump as claimed in claim .1, wherein said crests of the cam are plane.
  • Rotary displacement pump as claimed in claim 1, wherein the means biasing each closing member is a spring.
  • Rotary displacement pump as claimed in claim 1, comprising two diametrically opposed closing members coacting with each cam, said biasing means comprising a single annular spring ⁇ mounted in the body to rock about an axis perpendicular to the diametrical plane intersecting the closing members and resiliently bearing against the diametrically opposed closing members, whereby the spring is not subjected to variations in bending stress.
  • Rotary displacement pump as claimed in claim 1, wherein said inlet ports and discharge ports are respectively located adjacent and on opposite sides of said closing members.
  • each closing member comprises a recess adjacent the discharge port for the passage of fluid under pressure from the pump chambers to the end of the closing member remote from the end thereof in contact with the cam, whereby the pressure of said fluid 'biases the closing member into contact with the corresponding cam.
  • Rotary displacement pump also of utility as a fluid motor, said pump comprising a fixed part and a rotating part, said fixed part comprising a pump body having an axis, said rotating part consisting of a single rotor mounted in said body torotate about said axis and means for driving said rotor in rotation, said rotor having at each end thereof an annular face cam, said body having inner annular end faces respectively cooperative with said cams, each cam having a progressively varying profile defining three recess portions and three plane crests spaced apart, said crests being in sliding contact with said annular end faces whereby said recess portions of each cam define with said body three pump chambers which rotate with said rotor, four closing members mounted in said body to slide in a direction substantially parallel to said axis, two of said closing members being diametrically opposed and cooperative with one of said cams and two of said closing members being diametrica'lly opposed and cooperative with the other of said cams, elastically yieldable means biasing said closing members against said cam

Landscapes

  • 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)
US524418A 1965-02-04 1966-02-02 Rotary volumetric pump Expired - Lifetime US3404632A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR4361A FR1458112A (fr) 1965-02-04 1965-02-04 Pompe volumétrique rotative

Publications (1)

Publication Number Publication Date
US3404632A true US3404632A (en) 1968-10-08

Family

ID=8570006

Family Applications (1)

Application Number Title Priority Date Filing Date
US524418A Expired - Lifetime US3404632A (en) 1965-02-04 1966-02-02 Rotary volumetric pump

Country Status (6)

Country Link
US (1) US3404632A (OSRAM)
CH (1) CH453905A (OSRAM)
DE (1) DE1553176A1 (OSRAM)
FR (1) FR1458112A (OSRAM)
GB (1) GB1139451A (OSRAM)
SE (1) SE329771B (OSRAM)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3751194A (en) * 1971-01-14 1973-08-07 J Marcel Rotary devices operated by pressurized-fluid
US3773022A (en) * 1972-01-17 1973-11-20 C Constantinou Rotary engine
US4181480A (en) * 1977-08-17 1980-01-01 Balsiger Harold E Rotary blade hydraulic motor with fluid bearing
US20030138340A1 (en) * 2001-06-04 2003-07-24 Young-Jong Kim Cylinder assembly of compressor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5980225A (en) * 1996-07-05 1999-11-09 Sundstrand Fluid Handling Corporation Rotary pump having a drive shaft releasably connected to the rotor

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8893A (en) * 1852-04-20 Rotary
US878600A (en) * 1907-03-27 1908-02-11 Reinold Berrenberg Rotary pump.
US1686767A (en) * 1927-03-31 1928-10-09 Saxon James Anglo Rotary internal-combustion engine
US1936467A (en) * 1932-04-01 1933-11-21 James Schofield Rotary pump
US2672099A (en) * 1950-10-16 1954-03-16 Deubel Joseph Rotary pumping apparatus
US2812719A (en) * 1954-07-20 1957-11-12 Humphrey L Nash Jr Rotary pump
US2925779A (en) * 1955-12-21 1960-02-23 Standard Res Consultants Inc Rotary pump

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8893A (en) * 1852-04-20 Rotary
US878600A (en) * 1907-03-27 1908-02-11 Reinold Berrenberg Rotary pump.
US1686767A (en) * 1927-03-31 1928-10-09 Saxon James Anglo Rotary internal-combustion engine
US1936467A (en) * 1932-04-01 1933-11-21 James Schofield Rotary pump
US2672099A (en) * 1950-10-16 1954-03-16 Deubel Joseph Rotary pumping apparatus
US2812719A (en) * 1954-07-20 1957-11-12 Humphrey L Nash Jr Rotary pump
US2925779A (en) * 1955-12-21 1960-02-23 Standard Res Consultants Inc Rotary pump

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3751194A (en) * 1971-01-14 1973-08-07 J Marcel Rotary devices operated by pressurized-fluid
US3773022A (en) * 1972-01-17 1973-11-20 C Constantinou Rotary engine
US4181480A (en) * 1977-08-17 1980-01-01 Balsiger Harold E Rotary blade hydraulic motor with fluid bearing
US20030138340A1 (en) * 2001-06-04 2003-07-24 Young-Jong Kim Cylinder assembly of compressor

Also Published As

Publication number Publication date
CH453905A (fr) 1968-03-31
DE1553176A1 (de) 1970-12-03
FR1458112A (fr) 1966-03-04
SE329771B (OSRAM) 1970-10-19
GB1139451A (en) 1969-01-08

Similar Documents

Publication Publication Date Title
US3289542A (en) Hydraulic motor or pump
US2832293A (en) Vane pump
US3106163A (en) Pumps, motors and like devices
US3642390A (en) Vane-type rotary fluid-displacing machine
CA1073742A (en) Gerotor gearset device
US3034448A (en) Hydraulic pump
US3008424A (en) Hydraulic wheel
US3270681A (en) Rotary fluid pressure device
US3699845A (en) Rotary hydraulic pumps and motors
US2790391A (en) Two stage variable delivery vane-type pump
US3404632A (en) Rotary volumetric pump
US2985110A (en) Pump construction
GB1419171A (en) Rotary abutment positive displacement device
US3007419A (en) Positive displacement pump
US3188969A (en) Hydraulic pump or motor
GB1308390A (en) Hydraulic motor
US4082480A (en) Fluid pressure device and improved Geroler® for use therein
US2255786A (en) Reversible vane type fluid motor
GB1481911A (en) Hydraulic device with rotor seal
US3352247A (en) Fluid pressure device with dual feed and exhaust
US3869228A (en) Axial pressure balancing means for a hydraulic device
US3791779A (en) Pump rotor adjustment mechanism
US4181480A (en) Rotary blade hydraulic motor with fluid bearing
JPS58220987A (ja) ゲロ−タ型の液圧モ−タ又はポンプ用ロ−タリバルブ
GB1341414A (en) Variable displacement vane-type rotary pumps or motors