US3381891A - Multi-chamber rotary vane compressor - Google Patents

Multi-chamber rotary vane compressor Download PDF

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Publication number
US3381891A
US3381891A US531228A US53122866A US3381891A US 3381891 A US3381891 A US 3381891A US 531228 A US531228 A US 531228A US 53122866 A US53122866 A US 53122866A US 3381891 A US3381891 A US 3381891A
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Prior art keywords
compressor
inlet
chambers
rotor
outlet
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Expired - Lifetime
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US531228A
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English (en)
Inventor
Friedrich O Bellmer
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Edison International Inc
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Worthington Corp
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Priority to US531228A priority Critical patent/US3381891A/en
Priority to FR96978A priority patent/FR1512886A/fr
Priority to CH307167A priority patent/CH463683A/de
Application granted granted Critical
Publication of US3381891A publication Critical patent/US3381891A/en
Assigned to STUDEBAKER-WORTHINGTON, INC., A CORP. OF DE. reassignment STUDEBAKER-WORTHINGTON, INC., A CORP. OF DE. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: WORTHINGTON CORPORATION
Assigned to EDISON INTERNATONAL, INC. reassignment EDISON INTERNATONAL, INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: STUDEBAKER-WORTHINGTON, INC., A CORP. OF DE
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    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3446—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 F04C18/08 or F04C18/22 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

Definitions

  • ABSTRACT OF THE DISCLOSURE A rotary sliding vane compressor having multiple compression chambers circumferentially spaced within the rotor housing with groups of chambers serially connected to provide pressure staging.
  • this invention relates to a new and improved multi-chamber rotary vane compressor and more particularly to a multi-chamber rotary compressor which can achieve single or plural stage compression with only a single rotor and is sufi'iciently versatile that while operating as a single stage compressor, it can be unloaded in a simple and easy manner.
  • a two or three stage compressor of this kind has two or three separate rotors in separate housings which cause enormous bearing and machining problems and higher weight and space requirements, resulting in very high production costs.
  • the vane wear is higher in the high pressure stages because of high load and high temperature.
  • the lifetime of the vanes is substantially less than that of those in the low pressure stages and, accordingly, vanes in one portion of the compressor must be changed while others, in the low pressure stages, need not be changed which thus requires frequent servicing of the compressor.
  • the present invention contemplates a multi-chamber rotary vane compressor in which the rotor is perfectly balanced when running as a single stage compressor and, thus, the only forces thereon are in torque, and there is no side thrust as is found in conventional single-chamber rotary vane compressors.
  • the multi-cham-ber compressor of the present invention includes the well known advantages of compactness while additionally providing flexibility as the compressor can be easily adapted for compounding or conversion from a single stage to a two, three, or more stage compressor. Even when utilized as a plural stage compressor, there is equal wear on all of the vanes Whether they are running in high or low pressure stages. This increases the lifetime of the vanes.
  • Another object of this invention is the provision of a new, more versatile, and less expensive multi-chamber rotary vane compressor which can beconverted from single stage compression to two or more stages of compression.
  • Still another object of this invention is the provision of a new and better multi-chamber rotary vane compressor in which the vanes will have equal wear thereon whether the compressor is operating as a single stage or multi-stage unit.
  • a further object of this invention is the provision of a new and better rotary vane compressor which can be unloaded in a simple and easy manner and, additionally, can be converted from a single stage to a plural stage operation.
  • FIGURE 1 is an elevational view of a multi-chamber single stage compressor built in accordance with the principles of the present invention.
  • FIGURE 2 is a longitudinal sectional view of the compressor of FIGURE 1 taken through the compressor portion of the unit shown in FIGURE 1.
  • FIGURE 3 is a cross-sectional view of the compressor of FIGURE 1 taken along lines 3--3.
  • FIGURE 4 is a cross-sectional view of the apparatus of FIGURE 1 taken along lines 4-4.
  • FIGURE 5 is a cross-sectional view of the apparatus of FIGURE 1 taken along lines 5-5.
  • FIGURE 6 is a schematic diagram of the single stage compressor of FIGURES 1-5.
  • FIGURE 7 is a cross-sectional view similar to FIG- URE 5 of a modified compressor built in accordance with the principles of the present invention.
  • FIGURE 8 is a longitudinal elevational view of a multi-chamber two stage compressor built in accordance with the principles of the present invention.
  • FIGURE 9 is a longitudinal section through the second stage of the compressor of FIGURE 8.
  • FIGURE 10 is a cross-sectional View taken along lines 1010 of FIGURE 8.
  • FIGURE 11 is a cross-sectional view taken along lines 1111 of FIGURE 8.
  • FIGURE 12 is a cross-sectional view taken along lines 1212 of FIGURE 8.
  • FIGURE 13 is an enlarged sectional view of the closing means shown in FIGURE 12.
  • FIGURE 14 is a cross-sectional view similar to FIG- URE 12 of a modified form of the end cover for a two stage compressor similar to a two stage compressor shown in FIGURES 8l3.
  • FIGURE 15 is a schematic diagram of the compressor of FIGURES 8-l3.
  • FIGURE 16 is a cross-sectional view of a three stage compressor built in accordance with the principles of the present invention.
  • FIGURE 17 is a schematic showing of the compressor of FIGURE 16.
  • FIGURE 18 is a schematic showing of a modified form of the compressor of FIGURES 16 and 17.
  • FIGURE 19 is a schematic showing of a revised form of the compressor of FIGURES 16, 17 and 18.
  • FIGURE 1 there is shown a motor driven multichamber single stage compressor built in accordance with the principles of the present invention and generally designated by the numeral 20.
  • the motor driven compressor 20 includes a motor casing 22 and a compressor casing 24 within which are mounted respectively, the motor (not shown) and the compressor 26 driven thereby.
  • the motor casing 22 has a fluid inlet 28 through which the fluid to be compressed is passed.
  • the inlet 28 normally is utilized to pass therethrough refrigerant which will cool the motor within the casing 22 and, thereafter, be compressed within the compressor 26.
  • the motor drives a shaft 30 which has mounted thereon a rot-or 32 which forms the single rotor for the compressor 26.
  • the rotor 32. is mounted on bearings 34 and 36, which. bearings are respectively supported at the ends of the rotor 32 by an inwardly extending extension of the casing 24 and an end cover 38 forming a part of the casing 24.
  • the end cover 38 has a discharge opening 40 out of which the compressed refrigerant passes after having been compressed within the compressor 26.
  • the casing 24 has fixed therewithin a rotor housing 42 contiguous with the inner surface of the casing 24 and having its end closest to the motor covered by a suitable inlet plate 44.
  • the inlet plate 44 has three inlet openings 46, 48, and as best shown in FIGURE 4 which inlet openings are aligned with axially extending inlet passageways 52, 54, and 56 respectively.
  • the inlet passages 52, 54, and 56 are formed in the rotor housing 42.
  • the interior surface of the rotor housing 42 forms a cavity within which the rotor 32 can rotate with its surface touching three axially extending parallel lines on the interior of the rotor housing 42 and having arcuate recesses on the interior of the rotor housing 42 so that there will be defined between the surfac of the rotor 32 and the interior of the rotor housing 42 three compression chambers 58, 60, and 62 respectively positioned equidistant from one another.
  • Each of the inlet passageways 52, 54 and 56 is in communication with one end of its associated respective chamber 58, 60, and 62 through slots 64 formed in the rotor housing 42.
  • the rotor 32 has twelve vanes 66 positioned within radial slots 68 equally spaced about the circumference of the rotor 32. Vanes 66 and their associated slots 68 extend the length of the rotor 32.
  • each chamber 58 and and 62 opposite from the inlets 52, 54, and 56 there are positioned outlet passageways 70, 72, and 74 which communicate with the interior of the rotor housing 42 through slots 76, 78, and 80.
  • the longitudinally extending passageways 70, 72, and 74 are all in communication with a continuous passageway 82 in the end plate 38 which communicates with discharge opening 40.
  • the compressor housing 24 has a suction inlet 84 therein adjacent the inlet plate 44, which suction inlet is in communication with a passageway 86 which passageway connects the inlet openings 46, 4S, and 59.
  • Refrigerant fluid enters suction inlet 84, and is distributed through the passageway 86 and inlet plate openings 46, 48, and 58 into inlet passageways 52, 54, and 56 respectively. Thence, the refrigerant passes through the slots 4 into the compressor chambers 58, 60, and 62.
  • adjacent vanes 66 in cooperation with the rotor 32 and rotor housing 42 will form fluid transfer pockets to compress the refrigerant fluid in the usual manner of a rotary vane compressor, said vanes being forced outwardly by centrifugal force to conform to the inner surface of the rotor housing 42.
  • the fluid transfer pockets approach their maximum volumetric capacity adjacent inlet slots 62 and approach their minimum volumetric capacity adjacent outlet slots 76, 78, and 80.
  • the compressed refrigerant is forced through the slots 76, 78, and into the discharge passageways 70, 72, and 74 respectively. Thence, the now compressed fluid will pass through the outlet passageway 82 to the discharge outlet 40.
  • each one of the chambers 58, 60, and 62 will be reacting in the same manner, at the same time, so that there will be no rotor imbalance and no side thrust on the bearings 34 and 36.
  • FIGURE 7 there is shown a modified form of the compressor 26 end cover in a cross-sectional view similar to FIGURE 5.
  • This compressor 26' is modified by the addition of a second inlet opening 88 into the inlet passageway 50 (not shown).
  • the inlet opening 88 is connected to an extension 90 of the passageway 82' which extension 90 connects end cover opening 88 with passageway 72'.
  • a plug 92 which eflectively closes the passageway 90.
  • the plug 92 can be withdrawn for purposes which will be shown hereinafter with respect to FIGURES 9-13.
  • FIGURE 8 there is shown the multi-cham-ber compressor 26' of FIGURE 7 connected up as a two stage compressor.
  • Compressor 26 is like the compressor 26' discussed in FIGURE 7 except that the plug 92 has been screwed out to leave an open plug position 96, whereas the plug positioned 94 has been filled by screwing the plug 98 into place. Further, the plate 44 has been modified by eliminating the inlet opening 50 to the inlet passageway 56. This has produced a new inlet plate 44' as shown in FIGURE 11 having only two openings 46' and 48' which operated in a manner exactly like the inlets 46 and 48 described with respect to FIGURE 4. The end cover 38 is exactly like the end cover described in FIGURE 7.
  • FIGURE 15 which describes the operation of a compressor 26'.
  • refrigerant fluid enters the suction inlet 84, and is distributed through the passageway 86 to the openings 46' and 48' in the plate 44'.
  • the plate 44' prevents fluid from entering the compression chamber 62. from the passageway 86, but rather, the fluid enters the passageways 52 and 54 into the compression chambers 58 and 60. After compression within the chambers 58 and 60, the fluid is forced out of the openings 70 and 72 into the passageway 82.
  • the plug 98 prevents fluid leaving the passageways 70 and 72 from passing directly out the compressor outlet 40, but, instead, this fluid passes through the extension 92 into the inlet 88 of compressor chamber 62 which will then further compress the fluid before it is passed out of the compression chamber 62 through outlet 74 to the compressor outlet 40. Accordingly, with a single rotor, it has been possible to achieve two stage compression of the refrigerant fluid while maintaining a balanced rotor.
  • vanes 66 during their travel through the compression chambers 58, 60 and 62 will be equally worn as they will pass through both the high pressure compression stage 62 as well as the low pressure compression stages 58 and 60 and, accordingly, there will be even wear thereon.
  • FIGURE 14 there is shown a modified form of the end cover 38 shown in FIGURE 12 in which a more permanent form of the two stage compressor is shown in that the plugs 92 and 96 have been removed and the passageway opened and that portion of the passageway 82 which extended from outlet 70 to the outlet 40 has been closed.
  • a more permanent form of the two stage compressor is shown in that the plugs 92 and 96 have been removed and the passageway opened and that portion of the passageway 82 which extended from outlet 70 to the outlet 40 has been closed.
  • FIGURE 16 there is shown another form of the present invention generally designated by the numeral 100.
  • the compressor 100 is a six chamber, three stage unit having a single rotor 102, cylindrical in cross-section.
  • the rotor 102 has vanes 104 adapted to be thrown outwardly by centifugal force against the inner surface of a rotor housing 106.
  • the rotor housing 106 has a longitudinally extending cavity therein within which the rotor 102 rotates, which rotor 102 contacts the rotor housing within the cavity along six equally spaced parallel lines to define between the parallel lines six crescent shape chambers 108, 110, 112, 114, 116, and 118.
  • the chambers 103418 each have respective inlet passageways 120, 122, 124, 126, 28, and 130. Gases are exhausted from the chambers 108- 118 through exhaust ports 132 134, 136, 138, 140, and 142 respectively.
  • Exhaust ports 134, 136, and 138 are connected through a common conduit 144 to the common conduit 146 supplying inlet ports 128 and 130.
  • Outlet ports 1 10 and 142 are connected through a single passageway 148 to the inlet passageway 150 for inlet 120.
  • Inlet ports 122, 124, 126 are supplied through a common conduit 152 from a suction inlet 154.
  • refrigerant gas enters the suction inlet 154, passes through the common conduit 152 into the inlet ports 122, 124, and 126 respectively and thence to the compression chambers 110, 112, and 14 respectively.
  • the refrigerant fluid After compression in the chambers 110, 112, 114, the refrigerant fluid, now compressed, passes through the outlet ports 134, 136 and 138 through the common outlet conduit 144 to the common inlet conduit 146 for inlet ports 128, and 130.
  • the refrigerant fluid is further compressed and then forced out of outlet conduit 132.
  • the refrigerant fluid passing out of outlet conduit 132 has gone through three stages of compression. It will be understood that the refrigerant fluid will be compressed in each stage, thus requiring less volume and, accordingly, one less chamber for each stage of compression.
  • the vanes 10- will pass through the low pressure, medium pressure, and high pressure stages during each rotation of the rotor 102 and, accordingly, there will be equal wear on all of the vanes thus cutting down on unnecessary breakdowns of the compressor 100.
  • the compressor 100 could have been operated as a single stage compressor as shown in FIGURE 19 with all of the inlets 120-123 directly connected to the inlet port 154 and all of the outlet ports being connected together.
  • the compressor 100 can be operated as a two stage compressor as shown in FIGURE 18 wherein the compressor 100 is shown having four inlets 122, 124, 126', and 128 connected to the common inlet 154' to feed chambers 110, 112', 114', and 116 respectively.
  • the output ports 134', 136, 138 and 14-0 of chambers 110'116 are connected to the inlet ports 130' and 120' of chambers 118' and 108 respectively.
  • the outlet conduits 142' and 132' of chambers 118 and 108' respectively are connected together to form an outlet which will supply refrigerant fluid which has passed through two compression stages.
  • FIGURE 19 there are shown in the six compression chambers 108-118 with their inlets connected to the common suction inlet 154" through respective valves 160, 162, 164, 166, 168, and 170.
  • the outlets of each of the compression chambers 108-118 is connected a common outlet conduit 172.
  • the compressor shown in FIGURE 19 can be unloaded in a balanced manner by closing one or more of the valves 170. For example, if two of the valves 160 and 162 are closed, the compressor will be 67% loaded, with three valves closed the compressor will be 50% loaded, with four valves closed the compressor will be 33% loaded, etc.
  • the basic compressors shown in FIGURES 16- 19 can be operated as a single stage compressor with six chambers, capable of being unloaded to a varying extent, as noted in FIGURE 19; as a two stage compressor as shown in FIGURE 18; or as a three stage compressor as shown in FIGURES l6 and 17. All of this is achieved with a balanced rotor and with even wear of the vanes.
  • a multiple stage rotary compressor of the sliding vane type including:
  • said rotor and said housing inner wall defining a plurality of chambers equally spaced about said inner wall at one axial position along the rotor with each chamber being crescent-shaped and congruent to every other chamber, each chamber having an inlet port and an outlet port spaced therefrom;
  • said vane elements being radially movable whereby the volumetric capacity of said fluid transfer pockets approaches a maximum as said fluid transfer pockets communicate with said inlet ports and approaches a minimum as said fluid transfer pockets communicate with said outlet ports;
  • suction inlet means connected to the inlet ports of said first group of chambers.
  • the rotary compressor of the sliding vane type of claim 1 including:
  • the rotary compressor of the sliding vane type of claim 7 including selective connection means for effecting a change in said interconnection passageways to connect all of said inlet ports to said suction inlet means and all of said outlet ports to said compressor outlet means, to connect the outlet ports of certain chambers to the inlet ports of other chambers with the remaining outlet ports being conneced to the compressor outlet means and the remaining inlet ports connected to the suction inlet means, or to leave the interconnection passageways unelfected by said selective connection means.
  • a compressor comprising:
  • said cylindrical rotor being mounted for rotation within said cavity and defining with said housing inner wall a plurality of individual compression chambers equally spaced about said inner wall with each individual compression chamber being congruent to every other compression chamber and each compression chamber having an inlet port and an outlet port spaced therefrom,
  • compressor outlet means connected to the outlet ports of said second group of individual compression chambers
  • (k) compressor inlet means connected to the inlet ports of said first group of individual compression chambers.
  • interconnection passageways are further operative to connect the outlet ports of said second group of individual compression chambers to the inlet ports of a third group of individual compression chambers, the outlet ports of said third group of individual compression chambers being connected to said compressor outlet means, said third group of individual compression chambers being less in number than said second group of individual compression chambers.
  • the apparatus of claim 11 including selective connection means for varying said interconnection passageways to arrange a fourth and fifth group of individual compression chambers formed from the chambers forming said first and second and third groups, said fourth group outlet ports being connected to the inlet ports of said fifth group, said fifth group outlet ports being connected to said compressor outlet means and said fourth group inlet ports being connected to said compressor inlet means, said fourth group being greater in number than said fifth group.
  • a multiple stage rotary sliding vane compressor comprising:
  • vane elements being radially movable whereby the volumetric capacity of the fluid transfer pockets approaches a maximum as the transfer pockets communicate with the inlet ports and approaches a minimum as the fluid transfer pockets communicate with the outlet ports;
  • (h) means for connecting the inlets of a second group of the chambers in parallel to the outlets of the first group of chambers to form a second compression stage

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  • General Engineering & Computer Science (AREA)
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US531228A 1966-03-02 1966-03-02 Multi-chamber rotary vane compressor Expired - Lifetime US3381891A (en)

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Application Number Priority Date Filing Date Title
US531228A US3381891A (en) 1966-03-02 1966-03-02 Multi-chamber rotary vane compressor
FR96978A FR1512886A (fr) 1966-03-02 1967-03-01 Compresseur rotatif
CH307167A CH463683A (de) 1966-03-02 1967-03-02 Drehkolbenverdichter mit verschiebbaren Schaufeln

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US531228A US3381891A (en) 1966-03-02 1966-03-02 Multi-chamber rotary vane compressor

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Cited By (28)

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US3451614A (en) * 1967-06-14 1969-06-24 Frick Co Capacity control means for rotary compressors
US3730649A (en) * 1970-06-03 1973-05-01 Daimler Benz Ag Shift element for gas turbine for shifting between series and parallel operations
US3752605A (en) * 1971-11-17 1973-08-14 Borg Warner Rotary gas compressor
US3788770A (en) * 1972-06-15 1974-01-29 Gen Motors Corp Fluid pump with flow control means
US3981703A (en) * 1974-04-23 1976-09-21 Stal-Refrigeration Ab Multistage vane type rotary compressor
US4043704A (en) * 1974-08-05 1977-08-23 Uniscrew Limited Double-acting rotary expansible chamber pump adaptable to series or parallel operation
US4347044A (en) * 1978-08-18 1982-08-31 S.R.M. Hydromekanik Aktiebolag Pumps
US4589829A (en) * 1983-08-20 1986-05-20 Mitsubishi Denki Kabushiki Kaisha Vane pump
US4697994A (en) * 1983-12-28 1987-10-06 Seiko Seiki Kabushiki Kaisha Multistage discharge type rotary vacuum pump
US4778352A (en) * 1985-07-19 1988-10-18 Diesel Kiki Co., Ltd. Variable capacity vane compressor
DE3740696A1 (de) * 1987-12-01 1989-06-15 Erich Fuergut Fluegelzellenpumpe fuer gase, daempfe, oder dgl. druckmedien
US20050287019A1 (en) * 2004-06-25 2005-12-29 Calsonic Compressor Inc. Gas compressor
US20090035166A1 (en) * 2007-07-30 2009-02-05 Tecumseh Products Company Two-stage rotary compressor
WO2009145898A1 (en) 2008-05-29 2009-12-03 Flsmidth A/S Rotary sliding vane compressor
US20100139613A1 (en) * 2005-03-09 2010-06-10 Pekrul Merton W Plasma-vortex engine and method of operation therefor
ITTO20090705A1 (it) * 2009-09-16 2011-03-17 Vhit Spa Capsulismo, particolarmente per turbomacchine, turbomacchina comprendente tale capsulismo e gruppo rotante per tale capsulismo
US20110116958A1 (en) * 2005-03-09 2011-05-19 Pekrul Merton W Rotary engine expansion chamber apparatus and method of operation therefor
US20110142702A1 (en) * 2005-03-09 2011-06-16 Fibonacci International, Inc. Rotary engine vane conduits apparatus and method of operation therefor
US20110158837A1 (en) * 2005-03-09 2011-06-30 Fibonacci International, Inc. Rotary engine vane apparatus and method of operation therefor
US20110155096A1 (en) * 2005-03-09 2011-06-30 Fibonacci International, Inc. Rotary engine valving apparatus and method of operation therefor
US20110155095A1 (en) * 2005-03-09 2011-06-30 Fibonacci International, Inc. Rotary engine flow conduit apparatus and method of operation therefor
US20110165007A1 (en) * 2005-03-09 2011-07-07 Fibonacci International, Inc. Rotary engine vane head method and apparatus
US20110171051A1 (en) * 2005-03-09 2011-07-14 Fibonacci International, Inc. Rotary engine swing vane apparatus and method of operation therefor
US20110176947A1 (en) * 2005-03-09 2011-07-21 Fibonacci International, Inc. Rotary engine vane cap apparatus and method of operation therefor
US20110200473A1 (en) * 2005-03-09 2011-08-18 Fibonacci International, Inc. Rotary engine lip-seal apparatus and method of operation therefor
US8360760B2 (en) 2005-03-09 2013-01-29 Pekrul Merton W Rotary engine vane wing apparatus and method of operation therefor
US8800286B2 (en) 2005-03-09 2014-08-12 Merton W. Pekrul Rotary engine exhaust apparatus and method of operation therefor
FR3015584A1 (fr) * 2013-12-20 2015-06-26 Willy Delbarba Compresseur a palettes multi etages

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FR2762879A1 (fr) * 1997-04-30 1998-11-06 Valeo Seiko Compressors Sa Compresseur de gaz, en particulier pour appareil de climatisation de vehicule automobile
DE20006683U1 (de) * 2000-04-11 2001-08-16 Cooper Power Tools Gmbh & Co Luftmotor
DE102011078038B4 (de) * 2011-06-24 2014-01-09 Joma-Polytec Gmbh Flügelzellenpumpe

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US2569640A (en) * 1943-02-16 1951-10-02 Moore Inc Oscillating fluid pressure machine
US2570832A (en) * 1943-02-16 1951-10-09 Moore Inc Oscillating fluid pressure machine
US2565651A (en) * 1945-04-27 1951-08-28 Oilgear Co Sliding vane type hydrodynamic machine
US2832199A (en) * 1953-04-30 1958-04-29 American Brake Shoe Co Vane pump
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Cited By (49)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3451614A (en) * 1967-06-14 1969-06-24 Frick Co Capacity control means for rotary compressors
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Also Published As

Publication number Publication date
FR1512886A (fr) 1968-02-09
CH463683A (de) 1968-10-15

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