US3642390A - Vane-type rotary fluid-displacing machine - Google Patents

Vane-type rotary fluid-displacing machine Download PDF

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Publication number
US3642390A
US3642390A US855996A US3642390DA US3642390A US 3642390 A US3642390 A US 3642390A US 855996 A US855996 A US 855996A US 3642390D A US3642390D A US 3642390DA US 3642390 A US3642390 A US 3642390A
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Prior art keywords
profile
vane
sinuous
casing
internal
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US855996A
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English (en)
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Bernhard Nils Ostberg
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Priority claimed from AU43288/68A external-priority patent/AU423669B2/en
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    • 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
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • 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
    • F04C2/3446—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 the inner and outer member being in contact along more than one line or surface
    • 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
    • F04C2250/00—Geometry
    • F04C2250/30—Geometry of the stator
    • F04C2250/301—Geometry of the stator compression chamber profile defined by a mathematical expression or by parameters

Definitions

  • ABSTRACT [30] F reign Application Priority Data
  • a fluid-displacing machine has a rotor member and a stator Sept 12 1968 Australia 43 288/68 member relatively rotatable about a common axis.
  • One of the members has an internal peripheral profile that is sinuous, op- Nov. 8, 1968 Australia ..46,002/68 posed to which the other of the members hasva Peripheral profile that is circular.
  • the contour of the sinuous profile [52] us Cl tai generates an odd number of evenly spaced chambers inter- [51] Int Cl 2 3/00 6 5 6 5/00 posed by cam surfaces and is developed so that the diametral 58] Fie'ld 418/133 150 156 175, distance between its opposite profile surfaces is constant.
  • At 103/121 153- 9i/74 129 123 1 least one diametrally disposed vane is slidably mounted in the 8 circular member and adapted to continuously contact and sweep the sinuous profile surface of the other member, there being inlet and discharge passages leading into and out of each [56] Reerences cued chamber respectively whereby upon relative rotation of the UNITED STATES PATENTS members pumping and/or compressing action is promoted.
  • This invention relates to vane-type rotary fluid displacing machines, such as pumps and compressors, and has for its principal objective a machine of simple construction in which the rotor member and stator member are relatively rotatable about a common axis, either member being stationary and the other rotatable.
  • a subordinate objective is to provide a novel sealing device between the relatively moving contact surfaces of one said member and the vane or vanes carried by the other said member, which device also contributes to simplifying the manufacture of the machine.
  • the invention provides a vane-type rotary fluid displacing machine comprising an external member cooperating with an internal member, the members being relatively rotatable about a common axis, the external member having an internal peripheral surface and the internal member having an external peripheral surface, the surfaces being opposed, one of which peripheral surfaces has a sinuous profile developed so that the diametral distance between its opposite profile surfaces is constant, the other peripheral surface being circular, said surfaces defining between them a plurality of an odd number of evenly spaced chambers interposed by cam surfaces, at least one diametrally disposed vane slidably mounted in the circular member and adapted to continuously contact and sweep the profile surface of the other member, so that upon relative rotation of the members the or each vane slides in the circular member as the vane follows the profile surface, and inlet and discharge passages leading into and out of each chamber respectively, whereby fluid is alternately drawn into and discharged from the chambers by the sweeping action of the vane or vanes.
  • the external member or casing, has an internal peripheral surface following a sinuous profile defining a plurality of an odd number of evenly spaced outwardly extending chambers interposed by inwardly extending cam surfaces, the internal member being circular and having at least one diametrally disposed vane slidably mounted therein and adapted to continuously contact and sweep the casing profile.
  • the external member or casing, has a circular internal peripheral surface while the internal member has an external peripheral surface following a sinuous profile defining a plurality of an odd number ofevenly spaced inwardly extending chambers interposed by outwardly extending cam surfaces, there being preferably two diametrally opposed vanes slidably mounted in the casing. In this arrangement the two vanes would be rigidly connected so that they operate in unison.
  • a single diametrally disposed vane located in the internal member may be employed.
  • the contour of the profile surface will be such that the diametral distance between the opposite profile surface, i.e., the surfaces contacted by the vane or vanes, is constant.
  • FIGS. 1, 2, 3 and 4 illustrate the mathematical development of the contour of the profile surface of the device of the present application
  • FIG. 5 is a sectional elevation, taken along the line 55 of FIG. 6, of a basic form of pump or compressor, according to the invention
  • FIG. 6 is a sectional elevation taken along the line 6-6 of FIG. 5;
  • FIG. 7 is a sectional elevation taken along the line 77 of FIG. 8, ofa modified form of the machine
  • FIG. 8 is a sectional elevation, taken on the line 88 of FIG. 7;
  • FIG. 9 is an end elevation of a modified form of casing body
  • FIG. 10 is a sectional view, taken on the line 10--10 of FIG. 9.
  • FIGS. 11 and 12 indicate a further embodiment of the invention of the present application.
  • the contour of the profile surface may be developed according to the following mathematical formula, having reference to the accompanying diagrams designated FIG. 1, FIG. 2, FIG. 3 and FIG. 4:
  • FIG. 1 illustrates the development of a sinuous profile for one of the movable members of the present apparatus
  • FIG. 2 illustrates the trigonometric relationship of two points of the profile of FIG. 1
  • FIG. 3 illustrates a portion of the sinuous profile of FIG. 1, a second portion of a sinuous profile corrected for curvature of the vane of the present ap paratus
  • a third curve shows a portion of a sinuous profile corrected for a liner to be placed inside the sinuous profile
  • FIG. 4 shows an enlarged portion of FIG. 3.
  • Curve 3 described the shape of the contoured surface of the pump housing.
  • r be the radius vector defining the position of P the center of curvature of the vane end.
  • Curve 2 is traced out by curved surface of vane end.
  • Curve 3 is curve to be formed to allow for liner.
  • Line P,P P is at right angles to the tangent of each of the three curves.
  • This "single" vane may be in two radially extending portions stressed apart by resilient means to that the profilecontacting edges of the vane portions are constantly pressed against the profile surface to improve sealing.
  • the inwardly directed ends of the two portions of the vane are provided with interacting ratchetlike means whereby the composite vane can be extended lengthwise when in situ until the outwardly directed ends operatively contact the casing profile surface, the ratchet like means then preventing reversal of this movement so that the length of the vane is maintained independently of the resilient means.
  • Additional sealing means such as inlays of plastic material, may be employed at contact edges in known manner.
  • lt is a subordinate feature of the invention to provide a novel sealing device between the casing profile surface and the vane, which sealing device comprises a thin liner of resilient sheet material located within the casing adjacent the profile surface and conforming to the contour of the profile, the liner being separated from the profile face by a layer of elastic material, such as crepe rubber or plastic. Where very high temperatures are involved, this layer could be composed of asbestos.
  • the circular member has a flange at one or each side and the separating elastic layer in the profiled member is stressed laterally against the relatively moving surfaces of said flange or flanges, thus providing a seal along the sinuous
  • the centrifugal component acting upon the vane or vanes can create a serious problem, especially at speed, and at very high speeds can be prohibitive.
  • the, internal vane-carrying member can remain stationary, while the external casing (which carries no vanes) can rotate, thus entirely eliminating this problem.
  • the common axis of the casing and the internal member further simplifies this arrangement.
  • lnlet and outlet fluid ducts can, with simplicity, be via hollow central coaligned shafts supporting the internal member at each end, which member is stationary in this arrangement.
  • a pump or compressor according to the invention provides a simple valveless construction in which the direction of fluid flow through the machine is automatically reversed merely by reversing the direction of machine rotation.
  • a subordinate feature of the present invention is the provision of a novel sealing means for the relatively moving lateral surfaces of the machine.
  • the primary objective in endeavours to solve this problem has been a device that will automatically take up or accommodate lateral wear as it occurs.
  • a further desideratum is a device that will automatically increase the contact pressure between these relatively moving lateral surfaces with increase in the working pressure of the machine.
  • the said subordinate feature provides, in a rotary fluid-displacement machine according to the invention having an outer casing including a body portion and two primary end walls rigid with said body portion, and an internal member operating within said casing, said member and said casing being relatively rotatable, the characteristic of sealing means for the relatively moving lateral surfaces of the machine, said sealing means comprising a secondary end wall disposed against or integral with one lateral surface of said member and defining a space between said secondary end wall and one of said primary end walls, the member and secondary end wall having limited freedom of axial movement within said casing, said space being utilized to apply fluid pressure to the space side of said secondary end wall to press it against the member thereby pressing the member against the other one of the primary end walls to provide a pressure-assisted seal at said lateral surfaces.
  • the fluid pressure generated by the machine is employed to provide fluid pressure-assisted sealing and this is conveniently achieved by ducting affording fluid communication between the space and the pressure side of the machine.
  • the internal member is stationary and the outer casing rotates upon bearings integral with the primary end walls and journaled on the stationary shafts extending axially at each end of the internal member.
  • the casing has limited axial freedom to float" on he internal member so that the lateral surfaces can make sealing contact under fluid pressure in operation.
  • the secondary end wall is disposed on the discharge (pressure) side of the internal member and attached to or integral with the lateral surface of the member on that side thereof. It may be in the form ofa peripheral flange.
  • the periphery of the secondary end wall or flange extends into and in sliding engagement with a concentric circumferential recess formed in the interior periphery of the casing body. This recess provides a degree of axial freedom from the casing to allow of the pressure-assisted action as previously explained.
  • annular space or chamber between the secondary end wall and the adjacent primary end wall, and this space is in communication with the pressure fluid on the discharge side of the machine.
  • the annular space is also in communication with the outlet end of the hollow shaft, such communication being conveniently achieved by a hole, or holes, drilled through the shaft into its hollow interior and registering with the annular space.
  • the area of the secondary end wall which is subjected to hydrostatic pressure on the space side is considerably greater than the area thereof exposed to fluid pressure on the vane side (working side), since the greater part of the lateral area 7 on the vane side is taken up by the internal member carrying the vane, so that in operation the combined internal member and secondary end wall act as a differential piston axially slidable in the cylinderlike casing.
  • the casing is free to move axially in the stationary internal member so that the differential hydrostatic pressure acts to press the primary end wall at the inlet side of the machine continuously against the adjacent lateral surface of the internal member, thereby effecting a pressure contact seal between these lateral surfaces irrespective of any wear that may take place in this region.
  • FIG. 5 is a sectional elevation, taken on the line 5-5 of FIG. 6, of a basic form of pump or compressor, according to the invention
  • FIG. 6 is a sectional elevation taken on the line 66 of FIG.
  • FIG. 7 is a sectional elevation, taken on the line 7-7 of FIG. 8, ofa modified form of the machine
  • FIG. 8 is a sectional elevation, taken on the line 88 of FIG. 7,
  • FIG. 9 is an end elevation of a modified form of easing body
  • FIG. 10 is a sectional view, taken on the line 10-10 of FIG. 9.
  • a casing 10 is mounted for rotation on fixed coaxial shafts 12a and 12b integral with an internal member 14.
  • the casing 10 is conveniently built up of a casing body 11 and end walls 110 and 11b,
  • the body 11 has an internal peripheral surface following a sinuous profile defining three evenly spaced outwardly extending similar chambers 16, interposed by inwardly extending cam surfaces 18.
  • the internal member 14 has a body 13 with a circular periphery 17. which latter is in constant sliding contact with the cam surfaces 18. and has a diametral slot 19in which slot a single vane is slidably fitted.
  • the contour of the profile surface 15 is such that the distance between diametrically opposed profile surfaces is constant.
  • the single vane 20, which is of fixed length corresponding to the said constant distance, will, at each end, contact the profile surface 15 at all positions of rotation of the casing 10.
  • the fixed shafts 12a and 12b are hollow and so cored that the inlet passages 24 lead from one of the hollow shafts, for example 12a connected to a supply of fluid, and the discharge passage 28 lead to the other of the hollow shafts 12b for connection to a delivery line.
  • the fixed shafts 12a, 12b may be mounted in any suitable manner, such as on a frame 30.
  • Any convenient drive means for the casing 10 may be employed, such as by V-belt operating in the groove 32 and driven by an electric motor or other power source, not shown.
  • FIGS. 7 and 8 depict a preferred embodiment of the invention incorporating a novel lateral sealing means to be further described later.
  • the vane 120 consists of two equal, radially extending parts 120a and 120b, stressed apart by a resilient packer 36.
  • This packer 36 is preferably in the form of a rubber or thermoplastic rod or tube extending the full width of the vane 120, which packer when compressed takes an oval crosssectional shape as shown at 36 in FIG. 7.
  • the packer 36 serves to resiliently urge the ends of the vane parts 120a, 120b, respectively, against the inner profile 115 of the casing to ensure good sealing contact therebetween and automatically compensate for wear.
  • the casing 110 is build up of four members, viz a primary end Wall 1110, a casing body 111, a spacer ring 40, and a primary end wall 1 1 1b.
  • the internal member 114 has a hollow shaft 112a. communicating with inlet passages 124 leading to inlet ports 122 for supply of fluid to the chambers 116.
  • the body 113 of internal member 114 is provided with a flange 42, which constitutes a secondary end wall and conveniently is integral with or attached to a lateral face of the body 113 adjacent to, but spaced from, primary end wall 1l1b by an annular chamber 44.
  • the spacer ring 40 has an interior circumferential recess 46 to slidingly receive a peripheral portion 43 of the flange 42. This recess extends into a small matching rebate 48 in the casing body 111 to provide a degree of axial freedom for the cats ing relative to the flange 42 and the internal member 114.
  • the internal member 114 has a hollow outlet shaft [12h communicating with the annular chamber 44 by way of holes 50, and the annular chamber 44 is in fluid communication with the pressure side of the machine by way of ports 52.
  • the annular chamber 44 is subject to continuous hydrostatic pressure which varies directly as the fluid pressure generated by the machine.
  • the combined internal member 114 and secondary end wall 42 act as a differential piston, as hereinbefore explained, and the casing 110, having limited axial freedom of movement, is free to move axially on the shafts 112a, l12b of the stationary internal member 114 so that the differential hydrostatic pressure acts to press the inner surface of the primary end wall 111a continuously against the adjacent lateral surface of the body 113 of the internal member 114, thereby effecting a pressure contact seal between these lateral surfaces irrespective ofwear that may take place in this region.
  • the invention provides a novel sealing device between the profile surface of the casing body and the contacting ends of the vane, which device is particularly applicable where a single vane offixed length is employed.
  • This sealing device comprises a thin liner 60 of resilient sheet material, located within the casing body 211, adjacent the profile surface 215 and conforming to the contour of the profile, the liner being separated from the profile face 215 by a layer 62 of elastic material, such as rubber or synthetic plastic.
  • the liner 60 could be made of nylon or other suitable plastic; for heavier duty, spring brass or stainless steel would be suitable.
  • the vane (not shown) will be of such proportions and so stressed against the liner 60 that the latter is slightly distorted by the vane at all times, this distortion following the movement of the vane and ensuring good sealing between the vane ends and the liner.
  • the resilient liner 60 backed by the elastic layer 62, providing adequate and continuous sealing therebetween. It also automatically compensates for wear.
  • the thickness and nature of the layer 62 can be determined according to the class of work to be performed. However, to prevent the liner 60 from distorting unduly under internal pressure, thereby separating the liner from the vane, stop means may be provided. Such stop means could take the form of inserts of strips or bands 64 on nonelastic material interspersed in the elastic layer 62, but of lesser thickness than the layer, thereby limiting the movement of the liner 60 into the layer 62.
  • FIGS. 11 and 12 illustrate an alternative arrangement of the invention in which the external member is in the form ofa casing 210 having a circular internal peripheral surface 217, while the internal member 214 has an external peripheral surface following avsinuous profile 215 defining three evenly spaced inwardly extending similar chambers 216 interposed by three outwardly extending cam surfaces 218.
  • Two diametrally opposed vanes 220a and 22b are slidably mounted in the casing 210, said vanes being connected so that they operate in unison.
  • FIG. 12 shows schematically one way of connecting the two vanes 220a and 220b, for example by an external rigid link 250.
  • a vane-type rotary fluid displacing apparatus comprising, an external member and an internal member relatively rotatable about a common axis, said external member having an internal peripheral surface and said internal member having an external peripheral surface, said peripheral surface of one of said members having a circular profile and said peripheral surface of the other of said members having a sinuous profile of constant diameter between opposing surfaces thereof, whereby said peripheral surfaces form a plurality of an odd number of evenly spaced chambers interposed by cam surfaces between them; at least one diametrally disposed vane means slidably mounted in said member having a circular profile and having curved ends adapted to continuously contact the diametrally opposed surfaces of said member having a sinuous profile and sweep said surfaces of said member having a sinuous profile, whereby said vane slides in said member having a circular profile as a result of one surface of said member having a sinuous profile forcing said vane toward the diametrally opposite surface of said member having a sinuous profile; and inlet and discharge passages leading into and out of each
  • R said radius of curvature of said vane end.
  • t the thickness of said liner.
  • the external member is in the form of a casing and has a circular internal peripheral surface, while the internal member has an external peripheral surface following a sinuous profile defining three evenly spaced inwardly extending chambers interposed by three outwardly extending carn surfaces, there being two diametrally opposed vanes slidably mounted in the casing, said two vanes being connected so that they operate in unison.
  • the casing comprises a body portion and two primary end walls rigid with said body portion and two primary said end walls having inner lateral surfaces opposed to lateral surfaces of the internal member operating within said casing, characterized by pressure-assisted sealing means for relatively moving contacting faces of said lateral surfaces, said sealing means comprising a secondary end wall disposed against or integral with one lateral surface of said internal member and defining an annular space between said secondary end wall and one of said primary end walls, the internal member and secondary end wall having limited freedom of axial movement relative to said casing, said space being utilized to apply fluid pressure between said secondary end wall and said one of said primary end walls thereby pressing the other lateral surface of said internal member against the other of said primary end walls to provide a pressure-assisted seal at said relatively moving contacting faces of said lateral surfaces.
  • the external member is in the form of a casing and has an internal peripheral surface following a sinuous profile defining three. evenly spaced outwardly extending chambers interposed by three inwardly extending cam surfaces, the internal member being circular and having a diametrally disposed vane slidably mounted therein and adapted to continuously contact and sweep the casing profile.
  • the internal member is stationary and comprised of a circular body portion having a shaft extending axially from each end of said body portion, the axis of the shafts being coincident with the center of the circular body portion and said shafts being hollow, one of the hollow shafts serving as inlet means to the inlet passages of the machine and the other of the hollow shafts serving as outlet means from the discharge passages of the machine.
  • diametral vane is composed of two equal, radially extending portions stressed apart by resilient means so that profile-contacting edges of the vane portions are constantly pressed against the profile surface to improve sealing.
  • the resilient means comprises a rubber or synthetic plastic tube or rod extending transversely of the vane for the width of the vane.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Hydraulic Motors (AREA)
US855996A 1968-09-12 1969-09-08 Vane-type rotary fluid-displacing machine Expired - Lifetime US3642390A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AU43288/68A AU423669B2 (en) 1968-09-12 1968-09-12 Improved vane-type rotary fluid displacing machine
AU4600268 1968-11-08

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US3642390A true US3642390A (en) 1972-02-15

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US855996A Expired - Lifetime US3642390A (en) 1968-09-12 1969-09-08 Vane-type rotary fluid-displacing machine

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US (1) US3642390A (enrdf_load_stackoverflow)
JP (1) JPS5120727B1 (enrdf_load_stackoverflow)
DE (1) DE1946794A1 (enrdf_load_stackoverflow)
FR (1) FR2017937A1 (enrdf_load_stackoverflow)
GB (1) GB1258983A (enrdf_load_stackoverflow)
IE (1) IE34277B1 (enrdf_load_stackoverflow)
SE (2) SE364552B (enrdf_load_stackoverflow)

Cited By (13)

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US3955903A (en) * 1974-05-10 1976-05-11 Aranka Elisabeth DE Dobo Rotary piston engine with improved housing and piston configuration
US4028021A (en) * 1975-12-08 1977-06-07 Curtiss-Wright Corporation Rotary trochoidal compressor with compressible sealing
US4419059A (en) * 1981-08-10 1983-12-06 Whirlpool Corporation Nonsymmetric bore contour for rotary compressor
US4432711A (en) * 1980-11-07 1984-02-21 Nippon Soken, Inc. Vane pump with cylinder profile defined by cycloid curves
US4456441A (en) * 1982-02-23 1984-06-26 Aharon Zilinsky Rotary machine
RU2260128C2 (ru) * 2003-08-25 2005-09-10 Государственное образовательное учреждение высшего профессионального образования "Алтайский государственный технический университет им. И.И. Ползунова" (АлтГТУ) Двигатель внутреннего сгорания
WO2006005382A1 (de) * 2004-07-09 2006-01-19 Joma-Hydromechanic Gmbh Einflügelvakuumpumpe
US20060051228A1 (en) * 2004-09-07 2006-03-09 Hayes-Pankhurst Richard P Pumps
US20100028189A1 (en) * 2006-09-21 2010-02-04 Vhit S.P.A rotary pump with vanes
US20150078946A1 (en) * 2013-09-19 2015-03-19 Hella Kgaa Hueck & Co. Vane Pump
CN107061257A (zh) * 2017-06-21 2017-08-18 袁廷华 一种线性流量低噪音液体泵
US9850118B2 (en) * 2010-08-20 2017-12-26 Pepsico, Inc. Bag-in-box pump system
EP3299578A1 (en) * 2016-09-21 2018-03-28 Core Dynamics ApS Energy transformation device and pump and motor utilising said device

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JPS5082604A (enrdf_load_stackoverflow) * 1973-11-26 1975-07-04
IL62290A0 (en) * 1981-03-04 1981-05-20 Zielinsky A Rotary machine
IT1154602B (it) * 1981-12-14 1987-01-21 Barmag Barmer Maschf Pompa a celle, delimitate da palette
WO1984003329A1 (en) * 1983-02-24 1984-08-30 Nippon Piston Ring Co Ltd Rotor for vane pump and motor
FR2547622B1 (fr) * 1983-06-16 1985-11-22 Leroy Andre Machine volumetrique a surface statorique particuliere
DE3421374C1 (de) * 1984-06-08 1985-06-20 Skf Gmbh Lagereinheit mit integrierter Pumpe
GB2363428B (en) * 2000-06-14 2005-02-23 Dennis Baynes Rotating engine
JP5643923B2 (ja) * 2011-12-21 2014-12-24 株式会社リッチストーン ロータリカムリング流体機械
DE102015108924B4 (de) 2015-06-05 2017-04-13 Nidec Gpm Gmbh Mechanisch angetriebene Flüssigkeits-Verdrängerpumpe

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US3955903A (en) * 1974-05-10 1976-05-11 Aranka Elisabeth DE Dobo Rotary piston engine with improved housing and piston configuration
US4028021A (en) * 1975-12-08 1977-06-07 Curtiss-Wright Corporation Rotary trochoidal compressor with compressible sealing
US4432711A (en) * 1980-11-07 1984-02-21 Nippon Soken, Inc. Vane pump with cylinder profile defined by cycloid curves
US4419059A (en) * 1981-08-10 1983-12-06 Whirlpool Corporation Nonsymmetric bore contour for rotary compressor
US4456441A (en) * 1982-02-23 1984-06-26 Aharon Zilinsky Rotary machine
RU2260128C2 (ru) * 2003-08-25 2005-09-10 Государственное образовательное учреждение высшего профессионального образования "Алтайский государственный технический университет им. И.И. Ползунова" (АлтГТУ) Двигатель внутреннего сгорания
WO2006005382A1 (de) * 2004-07-09 2006-01-19 Joma-Hydromechanic Gmbh Einflügelvakuumpumpe
USRE44841E1 (en) * 2004-09-07 2014-04-15 Quantex Patents Limited Pump with conveying chamber formed in outer rotor surface
US20060051228A1 (en) * 2004-09-07 2006-03-09 Hayes-Pankhurst Richard P Pumps
USRE47590E1 (en) * 2004-09-07 2019-09-03 Quantex Patents Limited Pump with conveying chamber formed in outer rotor surface
US7674100B2 (en) * 2004-09-07 2010-03-09 Pdd Innovations Ltd. Pump with conveying chamber formed in outer rotor surface
US8087915B2 (en) * 2006-09-21 2012-01-03 Vhit S.P.A. Rotary pump with vane support divided into two half shells
US20100028189A1 (en) * 2006-09-21 2010-02-04 Vhit S.P.A rotary pump with vanes
US9850118B2 (en) * 2010-08-20 2017-12-26 Pepsico, Inc. Bag-in-box pump system
US20150078946A1 (en) * 2013-09-19 2015-03-19 Hella Kgaa Hueck & Co. Vane Pump
CN104454514A (zh) * 2013-09-19 2015-03-25 黑拉许克联合股份有限公司 叶片泵
JP2015059572A (ja) * 2013-09-19 2015-03-30 ヘラ・カーゲーアーアー・ヒュック・ウント・コンパニー ベーンポンプ
US9765775B2 (en) * 2013-09-19 2017-09-19 Hella Kgaa Hueck & Co. Vane pump
CN104454514B (zh) * 2013-09-19 2018-07-03 黑拉许克联合股份有限公司 叶片泵
EP3299578A1 (en) * 2016-09-21 2018-03-28 Core Dynamics ApS Energy transformation device and pump and motor utilising said device
CN107061257A (zh) * 2017-06-21 2017-08-18 袁廷华 一种线性流量低噪音液体泵

Also Published As

Publication number Publication date
IE34277B1 (en) 1975-04-02
JPS5120727B1 (enrdf_load_stackoverflow) 1976-06-28
DE1946794A1 (de) 1970-09-10
GB1258983A (enrdf_load_stackoverflow) 1972-01-05
SE364552B (enrdf_load_stackoverflow) 1974-02-25
SE371864B (enrdf_load_stackoverflow) 1974-12-02
FR2017937A1 (enrdf_load_stackoverflow) 1970-05-22
IE34277L (en) 1970-03-12

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