US3748068A - Rotary vane device - Google Patents

Rotary vane device Download PDF

Info

Publication number
US3748068A
US3748068A US00227384A US3748068DA US3748068A US 3748068 A US3748068 A US 3748068A US 00227384 A US00227384 A US 00227384A US 3748068D A US3748068D A US 3748068DA US 3748068 A US3748068 A US 3748068A
Authority
US
United States
Prior art keywords
vane
vanes
rotor
main chamber
follower means
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
US00227384A
Other languages
English (en)
Inventor
L Keller
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.)
Keller Corp
Original Assignee
Keller Corp
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 Keller Corp filed Critical Keller Corp
Application granted granted Critical
Publication of US3748068A publication Critical patent/US3748068A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • 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
    • F01C1/352—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 vanes being pivoted on the axis of the outer member
    • 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
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0836—Vane tracking; control therefor by mechanical means comprising guiding means, e.g. cams, rollers

Definitions

  • ABSTRACT An eccentric rotor vane device that may be employed as pumps, including compressors; or engines, including motors, characterized by an improved seal structure; in addition to conventional main chamber; first and second ports communicating with the main chamber; a plurality of angularly related radial vanes, independently pivotal and rotatable about a vane axis within the main chamber; a rotor that is eccentrically mounted with respect to the main chamber; and a power delivery shaft connected with the rotor.
  • the improved seal means in a specific embodiment, comprises cylindrical vanes guides of the rotor'engaging concave faces of adjacent vanes on either side such that the vane guide is maintained in substantially uniform engagement with the vane lateral faces as it traverses radially inwardly and outwardly therealong during rotation of the rotor such that a satisfactory seal is maintained intermediate the vane guide and the vanes so that the vane guide can serve as a piston as well as an interdigitating means for effecting a change in volume of a subchamber defined intermediate the respective vanes, vane guides, andmain chamber.
  • This invention relates to rotary vane, or rotor vane, devices that may be employed as either pumps, including compressors, or engines, including motors. More particularly, this invention relates to an improvement in eccentric rotor, concentric vane devices that may be employed as pumps for pumping incompressible flu'ids or compressing and pumping compressible fluids; or as engines, including motors powered by either compressible or incompressible fluids and engines powered by internal combustion of a fuel using either the spark ignition cycle or the diesel cycle.
  • the seal means attempted have either allowed too much leakage to be practical or have imposed too much frictional resistance to movementto allow the machine sufficient mechanical efficiency to be pracitcaL
  • FIG. I is an isometric view of an air compressor in accordance with one embodiment of this invention.
  • FIG. 2 is an exploded view of the embodiment of FIG. .1.
  • FIG. 3 is a partial side elevational view of the main chamber, vanes and rotor subassemblies, with the end cover of the rotor removed; all of the embodiment of FIG. 2.
  • FIG. 4 is a partial isometric view, partly exploded, illustrating the vanes and the vane shaft of the embodiment of FIG. 3.
  • FIG. 5 is a paritalcross sectional view illustrating the discharge port and'chamber of the embodiment of FIG. 1.
  • FIGS. 6A and 6B are front and side views' of the sleeve containing the discharge apertures of the embodiment of FIG. 5.
  • FIG. 7 is a partial cross sectional view illustrating one type of seal intermediate the outermost end of the vane and the main housing, in accordance with another embodimentof this invention.
  • FIG; 8 is a partial cross sectional view illustrating still another type of seal intermediate the outer end of the vanes and the main housing.
  • FIG. 9 is a partial cross sectional view of one end of a vane guide retained in a circular plate of the rotor assembly in accordance with the embodiment of FIG. 2.
  • FIGS. 1-10 Referring now to the figures, and particularly, FIGS.
  • the air compressor, a rotor vane-device, 11 comprises a stator 13, a rotor assembly 15, FIG. 2, and a vane assembly;
  • the stator 13 includes a main body member 19 having a base or mounting bracket 21, FIG. 1.
  • the main body member 19 has peripherally disposed circular flanges 23, FIG. 2, that extend longitudinally for affixthe device is being employed as an engine or a pump and the nature of the fluid; for example, whether the fluid is compressible or not.
  • the intake port 31 comprises a plurality of elongate apertures 35-38 extending through the plates on both sides of the longitudinal cylindrical cavity 29; namely, end cap members 25 and 27 and the annular plates 39 and 41.
  • the elongate apertures 35-38 have a cross sectional shape commensurate with the subchamber defined intermediate the faces of the vanes and the respective vane guides and the inner wall 20, FIG.
  • a discharge port 33 is formed in the inner face of the body member 19 and extends from the rear, or about 280 position with respect to the top, clockwise toward the top.
  • the discharge port 33 has a series of elongate openings, illustrated in FIGS. 6A and 68. Ports having various other opening shapes may be employed if desired.
  • the main body memvided in the sleeve 93 may be retained in place within the longitudinal cavity 29 by means of cap screws inserted into apertures, such as aperture 113.
  • suitable splines may be employed to prevent the sleeve 93 from rotating, the spline being retained intermediate the respective annular plates 39 and 41.
  • the inlet ports 31 communicate with intake manifold 43, FIG. 1, to facilitate the connecting of the inlet to a source of the gas to be compressed; for example, a filter for ambient air.
  • the discharge ports 33 communicate with discharge manifold 45 to facilitate connection with a device or system using the compressed gas, or air.
  • a pair of cap members 25 and 27 are affixed to the opposite sides of the main body members 19, as by bolts or cap screws 47, FIGS. 1 and 2. Only a few of the cap screws are shown in FIG. 2 to prevent cluttering up the drawings. As, is well known, of course, the cap screws 47 engage, aligned bores in the cap members 25 and 27 and tapped bores in the flanges 23.
  • Coaxial bearing sleeves 49' and 51 are integrally formed with the cap members 25 and 27.
  • a thrust plate 53 is secured to the bearing sleeve 51 by suitable cap screws 55, with a suitable seal 57 sandwiched thereb'etween.
  • a coaxial collar 61 is secured by cap screws 63 to the outer end of bearing sleeve 49.
  • the coaxial collar 61 is disposed about a shaft extending therethrough and contains a suitable shaft seal 83. Suitable bearings are interposed intermediate the bearing sleeves and their respective shafts. The hearings will be appropriate to the use in which the rotor vane device is being employed. As illustrated, roller'bearings 59 are employed.
  • the rotor assembly 15 includes a pair of opposite and mating circular plates 65 and 67 that rotatably engage or proximate the circular apertures 68 and 70 in the annularplates 39 and 41. If desired, bearing materials can be provided at the interface between the respective circular plates 65 and 67 and the inner walls of apertures 68 and 70.
  • follower means such as the vane guides 69,
  • each subchamber is defined by a pair of confronting vane faces on its sides, by a vane guide and the interior surface of the main chamber at its inner and outer boundaries, and the annular plates 39 and 41 at its ends.
  • Each subchamber varies from a minimum volume at the outermost, or 0, position of the vane guide to a maximum at the 180", or innermost, position of the vane guide 69.
  • each respective vane guide may be cantilevered from a single circular plate; although having two circular plates and having the vane guides affixed to each of the plates affords a reinforced structure that is, ordinarily, more advantageous.
  • the shaft 81 provides a better structure, but it may be omitted if a cantilevered structure is desired.
  • the vane guides 69 traverse inwardly and outwardly radially along the adjacent vanes to effect the improved seal, as described with respect to the vanes and the vane assembly later hereinafter.
  • Each of the illustrated follower means comprises a vane guide 69 that extends longitudinally along the rotor with vane engaging surfaces on each side that are disposed symmetrically about a central axis thereof.
  • Each of the vane engaging surfaces of a vane guide 69 has the same predetermined radius of curvature with respect to the central axis.
  • eah vane guide 69 comprises a cylindrical roller 71, FIGS. 2, 3 and 9, rotatably mounted on a shaft 73. Rotation of the cylindrical roller 71 is facilitated by suitable bearing means, such as insert 75.
  • Each shaft 73 is fixed between shoulders 77 of the circular plates 65 and 67 by cap screws 78 penetrating through apertures 80 in the circular plates 65 and 67, FIG. 9.
  • the respective follower means may be retained intermediate the circular plates 65 and 67 by any other conventional means.
  • the vane guide 69 may be integrally formed and the shaft portion 73 nested in suitable bearing means recessed in the circular plates 65 and 67.
  • the illustrated embodiment has been found to be preferred becuase of the advantages attendant the respective rolling friction instead of requiring a sliding friction. If the duty is unusually severe, the sleeve insert 75 may be replaced by aircraft roller bearings or needle bearings for still further improved performance.
  • a power shaft 79 isfixed to and extends coaxially from the circular plate 65 through roller bearings 59 in bearing sleeve 49. As indicated hereinbefore, it is journalled within coaxial collar 61 and shaft seal 83; and extends to a prime mover or other source of power.
  • a second shaft 81 extends coaxially from the circular plate 67 and is journalled for rotational movement in roller bearings 59 in bearing sleeve 51, to provide additional support to the rotor assembly. As indicated, the second shaft is not always necessary, particularly for light applications in which the respective vane guides 69 are cantilevered from a plate 65 carried by the power shaft 79.
  • each of the shafts 79 and 81 has a male threaded portion 85, FIG. 2, of reduced diameter that threadedly engages a tapped aperture in the respective circular plates 65 and 67.
  • the portion 85 pulls the sunk to keep the clearance intermediate the plates to a minimum.
  • aircraft type roller bearings are employed as the thrust bearings 87, although other bearings may be employed as appropriate to the use of the rotor vane device.
  • the bearings 87 provide improved structure and should not be omitted casually.
  • the vane assembly 17 is located in the longitudinal cavity 29 and, as depicted, includes a floating axle pin 89, FIGS. 2-4, that is substantially coaxial with the cylindrical cavity 29 and that extends between the circular plates 65 and 67.
  • a plurality of vanes 91 extend radially outwardly from axle pin 89 and are individually pivotal thereon.
  • each vane is provided with a curved end face 95 of substantially the same ra dius of curvature as the inside wall 20 of the sleeve 93 which defines the internal surface of the vane assembly cavity 100.
  • each vane 91 is in substantial sliding engagement with the sleeve 93 such that it forms a satisfactory seal for'confming the fluid inthe respective v subchamber on either side thereof.
  • the seal intermediate the vanes 91 and the sleeve 93 have not been particularly critical becuase the differential pressure between adjacent subchambers is not inordinately high and because the centrifugal force on the vanes tend to retain sufficient sealing engagement between the respective vane ends 95 and the sleeve 93. Any type of seal appropriate to the use may'be employed. Two other types of seals are illustrated in FIGS. 7 and 8.
  • a separate seal 97 is fitted on the vane '91 before the v aneassembly is emplaced within the sleeve '93.
  • the separate seal 97 slidhas a knuckle 103a that is twice as wide as ordinary and is centrally disposed.
  • the vanes may have their respective knuckles disposed at onehalf of the axle pin 89 plus the thickness of one knuckle and intermeshed such that the use of the wide central knuckle 103a is obviated.ln fact, any other method of supporting the vanes that will allow the interdigitating thereof may be employed.
  • the vanes' are accelerated and decelerated during rotation, symmetrical arrangement of knuckles with respect to a transverse plane through the vane center ispreferable, as illustrated in FIG. 4.
  • the respective vanes 91 have lateral faces 105 that are concaved inwardly toward the central plane of the vane such that the respective followers, or vane guides, 69 are maintained in substantially uniform sealing engagement with the vane lateral faces 105 as the vane guides 69 traverse radially inwardly and outwardly therealong during rotation of the rotor assembly 15.
  • substantially uniform sealing engagement is meant an engagement such that a satisfactory seal is maintained intermediate the respective vane guides 69 and the vanes 91 so that the vane guides 69 can serve aspistons as well as interdigitating means as they traverse radially inwardly and outwardly along the respective vanes 91.
  • the seal 97 may have -a lubricant such as a fluorocarbon impregnated thereinto for applications in which'a lubricant is not injected in an appreciable quantity.
  • a seal such as illustrated'inFlG. 8 is' employed for the so-called oilless” applications.
  • a separate seal element 99 is inset within an end 95 of the respective vanes 9].
  • Suitable biasing means such as a resilient annular pad 101 may be employed to bias the seal element 99 outwardly, in con junction with centrifugal force, to sealingly engage the sleeve 93.
  • each of -the vanes 91 has integrally formed with theinner end thereof at least one annular knuckle 103 that conformingly engages the axle pin 89.
  • the knuckles 103 are axially offset relative to. each other and are stacked on the axle pin 89 with their confronting faces in sliding engagement to permit the relative interdigitating, or rocking, of the vanes v91 about the axle pin 89.
  • the vane 93a These engines may be only about 4 inches in length and 6 inches in diameter, yet develop enough power'to operate a smal automobile.
  • the grinding of the vane faces is effected by moving the vanes and sized grinding rollers through 360 as the vanes would be moved by the rotor assembly 15, with increasing distances of eccentricity, up to the eccentricity actually employed in the device 11, of the shaft of the vane axle pin 89 and the axis of the shaft of the grinder rollers that is equivalent to the axis of the shafts 79 and 81 of the rotor assembly 15.
  • the respective subchambers are defined, as described hereinbefore, and take in the fluid through intake ports 31 as the respective vanes 91 are moved further apart by the inwardly radially traversing vane guides 69.
  • the respective intake ports communicate, by way of intake manifold 43 and suitable conduit, with a source of the gas to be compressed.
  • each inwardly traversing vane guide 69 further creates a larger subchamber to induce the fluid to flow into the vane assembly cavity 100 through the intake port 31.
  • the volume expansions-of the sum of the subchambers during a single rotation of the rotor exceeds the total volume of the cavity 100.
  • This particularly advantageous facet enables a wide variation in volumes and hence, an unusually large capacity of this positive displacement rotor vane device, as compared with the prior art devices.
  • the vane guides are able to move completely to the sleeve 93 in the position and reduce the volume of the subchamber to substantially zero, ornothing; and the vane guide moves inwardly substantially to the knuckles 103 of the vanes to create the maximum possible radial dimension for the respective subchamber at the 180 position.
  • FIG. 3 illustrates the closeness of the oppositely disposed faces of adjacent vanes at the top, or 0 position, as contrasted with the widely spaced apart facing surfaces of the vanes at the bottom, or 180 position.
  • the rotor forces the vane guides and consequently the vanes to rotate, expanding the subchambers and taking in an ever increasing amount of gas to proximate the lower position of the vanes, at the cut-off of the intake port 31. Further rotation of the rotor causes the respective vanes to begin to be moved closer together, compressing the fluid contained in the respective subchambers defined intermediate the adjacent vanes. As the fluid is compressed to the desired pressure, the respective subchamber will have been moved to the discharge apertures l l, at which point the fluid begins to flow from the subchamber. Substantially all of the fluid will have flowed from the subchamber as it moves to near the top. At the top, the respective vane guide will have been moved to the outermost pesition to reduce the volume of the subchamber to substantially zero, as can be seen in FIG. 3. Further rotation begins the intake cycle over again.
  • the materials of construction ordinarily employed in this art may be employed herein and no exotic new materials are necessary.
  • the structural strengths and the wearing properties of the materials that interfere together will be chosen appropriate to the application. For example, in certain applications it may be possible to employ plastics to reduce the friction as they interfere with adjacent metallic components. In general, we have been working with the most deleterious types of materials and have employed noncorrodible metals in those surfaces coming in contact with the fluids.
  • this invention provides a rotor vane device that achieves the objects delineated hereinbefore and obviates the disadvantages of the prior art devices. lts size and weight are unbelievably more compact and lighter than conventional air compressors.
  • roller vane guides with the attendant rolling friction, effects a long-wearing, trouble-free seal that is an important advance in the technology toimprove our-ecology, since the rotor vane device 11 makes practical essentially nonpolluting engines, when used as the expander in an external combustion Rankine cycle system.
  • the large changes in volume of the subchambers allow unusually large variation in compression ratios when the rotor vane device 11 is employed as an engine.
  • a main chamber having a substantially cylindrical interior surface
  • vanes c. a plurality of angularly related radial vanes, independently pivotal and rotatable within said main chamber about a vane axis therewithin; said vanes occupying substantially the total radial distance from said axis to said interior surface of said main chamber;
  • a rotor that is eccentrically mounted with respect to said main chamber and rotatable about a rotor axis spaced from said vane axis; said rotor having follower means for interdigitating said vanes and effecting a change in volume of a sub chamber intermediate respective said vanes as said rotor and said vanes are rotated within said main chamber; each sub chamber being delineated by a pair of confronting vane faces and a corresponding follower means between said vane faces and said main chamber interior surface and varying from a minimum volume at the radially outermost position of said follower means with respect to said vane axis, said minimum volume position being referred to as the position, to a maximum volume at the radially innermost position of said follower means, re-
  • said follower means is disposed intermediate said i z g respects) Sald respective vanes and comprises vane guides that P "9 e l t at each Sal respicuve are substantially cylindrical rollers extending longivane 'mamtafns S tudinally of said rotor and having respective vane spefctwe P m of Contact adlacem Vane engaging surfaces on each side that are disposed guldes- 1 t i ll about d h a da i d 2.
  • said vane guides are dius of curvature with resp ct t the nt l i f rotatably mounted in said rotor and intermediate reeach respective vane guide; and spective said vanes.
  • said vanes have lateral faces that are concaved in-

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US00227384A 1972-02-18 1972-02-18 Rotary vane device Expired - Lifetime US3748068A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US22738472A 1972-02-18 1972-02-18

Publications (1)

Publication Number Publication Date
US3748068A true US3748068A (en) 1973-07-24

Family

ID=22852890

Family Applications (1)

Application Number Title Priority Date Filing Date
US00227384A Expired - Lifetime US3748068A (en) 1972-02-18 1972-02-18 Rotary vane device

Country Status (3)

Country Link
US (1) US3748068A (ja)
JP (1) JPS554924B2 (ja)
SE (1) SE388461B (ja)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3883277A (en) * 1973-10-11 1975-05-13 Keller Corp Rotary vane device with improved seals
US3938918A (en) * 1974-04-16 1976-02-17 John Snygg Rotary vane device
US4902209A (en) * 1988-03-04 1990-02-20 Olson Howard A Sliding segment rotary fluid power translation device
US5575629A (en) * 1994-05-02 1996-11-19 Delaware Capital Formation, Inc. Vapor control system
US5850856A (en) * 1996-10-18 1998-12-22 Delaware Capital Formation, Inc. Gasoline dispenser with integral, internal self powered vapor recovery pump
US6018962A (en) * 1998-12-16 2000-02-01 American Standard Inc. Centrifugal compressor oil sump demister apparatus
US6659744B1 (en) * 2001-04-17 2003-12-09 Charles Dow Raymond, Jr. Rotary two axis expansible chamber pump with pivotal link
US10364826B2 (en) * 2013-02-20 2019-07-30 Carrier Corporation Inlet guide vane mechanism

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US32029A (en) * 1861-04-09 Chester l
US208298A (en) * 1878-09-24 Improvement in rotary engines
US308859A (en) * 1884-12-02 stewart
US1486906A (en) * 1921-07-05 1924-03-18 Joseph H Kolar Engine
US1535275A (en) * 1924-01-26 1925-04-28 Westin Oliver Peter Rotary pump
AT141416B (de) * 1933-06-28 1935-04-25 Jaro Dr Ing Zeman Kraft- oder Arbeitsmaschine mit vorwiegend drehender Bewegung.
US2049794A (en) * 1934-08-20 1936-08-04 James C Armor Pump
US2233534A (en) * 1938-08-26 1941-03-04 Arthur H Dettelbach Rotary pump

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US32029A (en) * 1861-04-09 Chester l
US208298A (en) * 1878-09-24 Improvement in rotary engines
US308859A (en) * 1884-12-02 stewart
US1486906A (en) * 1921-07-05 1924-03-18 Joseph H Kolar Engine
US1535275A (en) * 1924-01-26 1925-04-28 Westin Oliver Peter Rotary pump
AT141416B (de) * 1933-06-28 1935-04-25 Jaro Dr Ing Zeman Kraft- oder Arbeitsmaschine mit vorwiegend drehender Bewegung.
US2049794A (en) * 1934-08-20 1936-08-04 James C Armor Pump
US2233534A (en) * 1938-08-26 1941-03-04 Arthur H Dettelbach Rotary pump

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3883277A (en) * 1973-10-11 1975-05-13 Keller Corp Rotary vane device with improved seals
US3938918A (en) * 1974-04-16 1976-02-17 John Snygg Rotary vane device
US4902209A (en) * 1988-03-04 1990-02-20 Olson Howard A Sliding segment rotary fluid power translation device
US5575629A (en) * 1994-05-02 1996-11-19 Delaware Capital Formation, Inc. Vapor control system
US5816297A (en) * 1994-05-02 1998-10-06 Delaware Capital Formation, Inc. Vapor control system
US5904472A (en) * 1994-05-02 1999-05-18 Delaware Capital Formation, Inc. Vapor control system
US5850856A (en) * 1996-10-18 1998-12-22 Delaware Capital Formation, Inc. Gasoline dispenser with integral, internal self powered vapor recovery pump
US6018962A (en) * 1998-12-16 2000-02-01 American Standard Inc. Centrifugal compressor oil sump demister apparatus
US6659744B1 (en) * 2001-04-17 2003-12-09 Charles Dow Raymond, Jr. Rotary two axis expansible chamber pump with pivotal link
US10364826B2 (en) * 2013-02-20 2019-07-30 Carrier Corporation Inlet guide vane mechanism

Also Published As

Publication number Publication date
SE388461B (sv) 1976-10-04
JPS4890009A (ja) 1973-11-24
JPS554924B2 (ja) 1980-02-01

Similar Documents

Publication Publication Date Title
US4804317A (en) Rotary vane pump with floating rotor side plates
US6659744B1 (en) Rotary two axis expansible chamber pump with pivotal link
US3883277A (en) Rotary vane device with improved seals
US4191032A (en) Rotary energy-transmitting mechanism
US20050186100A1 (en) Spherical fluid machines
US3816039A (en) Rotary air pump with rotating and oscillating center piston
US3748068A (en) Rotary vane device
US3834840A (en) Compact reciprocating piston machine
US3816038A (en) Spherical displacement device and seal means therefor
US1994397A (en) Rotary engine
US4859163A (en) Rotary pump having vanes guided by bearing blocks
HU229249B1 (hu) Térfogatváltoztató forgó gép, elõnyösen kétütemû gömbmotor
US3139036A (en) Rotary piston action pumps
US2891482A (en) Rotary machine adapted to operate as a pump or as a fluid motor
US3574493A (en) Vane-type pumps
JPH01249973A (ja) スパイラル原理による圧送機械
US2880677A (en) Variable volume vane pump
US4219314A (en) Rolling piston rotary compressor
US3782107A (en) Air-cooled rotary internal combustion engine
US2487685A (en) Rotary oscillating vane pump
US4174195A (en) Rotary compressor and process of compressing compressible fluids
US2006298A (en) Rotary pump compressor, engine, and the like
US4239466A (en) Rotary machine with adjustable means for its eccentric rotor
US4370111A (en) Rotary pump or motor with drive rollers and free-floating rollers
US6145429A (en) Rotor assembly for rotary power device