US3269646A - Rotary compressor - Google Patents

Rotary compressor Download PDF

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Publication number
US3269646A
US3269646A US437956A US43795665A US3269646A US 3269646 A US3269646 A US 3269646A US 437956 A US437956 A US 437956A US 43795665 A US43795665 A US 43795665A US 3269646 A US3269646 A US 3269646A
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casing
eccentric
displacer
compressor
oil
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US437956A
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English (en)
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August Paul
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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
    • 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
    • F04C18/32—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F04C18/322—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member

Definitions

  • the main object of the invention is to improve the etiiciency and the antifrictional conditions of said rotary compressors by eliminating abrasion-causing oscillations of the driving shaft and of the gyratory displacer and by providing a continuously renewed oil hn on contacting or adjacent parts of the compressor, said oil film providing not only for a good lubrication and elicient sealing of the compressor, but also a distancing means between adjacent parts of the same.
  • the improved rotary compressor comprises a cylindrical casing, a central driving shaft rotatively mounted in the end walls of said casing, an eccentric xed on said shaft in said casing, at least one cavity formed in said eccentric in its portion of larger extension, bearing means arranged on said eccentricfor a cylindrical displacer, at least one annular cavity formed by said eccentric and within said displacer, a flywheel mass on said shaft in la portion of said annular cavity diametrically opposite said first-mentioned cavity for substantially balancing said portion of larger extension of the eccentric, a rib member radially projecting from said displacer into a recess provided in said casing, this recess forming near the inner wall of said casing a pair of opposite semi-cylindrical grooves for containing corresponding rotary guide members between which said rib member projects into a compression chamber formed by said recess beyond said grooves, said rib member acting as a pump piston in said compression chamber, air conducting means connecting said compressor chamber with an oil supply means and
  • the arrangement of the flywheel mass conveniently in such that the eccentric between its end portions which carry the bearings of the gyratory displacer provides for an annular cavity and that in this cavity at the side of its shorter extension the flywheel mass is Xed to the driving shaft.
  • the arrangement may also be such that only one bearing is provided in the middle of the eccentric and that the end portions of the latter form the cavities for two flywheel masses secured to the driving shaft.
  • the said cavities for the ywheel masses may be enlarged by inner recesses of the displacer body.
  • the cavity or cavities for housing the flywheel mass or masses may be formed in their major part in the displacer body.
  • the displacer in one or both end portions may be provided with annular recesses for facilitating the assembling of the eccentric, flywheel mass, bearings and displacer on the driving shaft within the compressor casing.
  • the said recess or compression chamber of the pump forms adjacent the inner wall of the cylindrical compressor casing a pair of opposite semi-cylindrical grooves for housing a pair of corresponding guide members for the rib member of the gyratory displacer, and each of these guide members is provided with a central longitudinal bore and with a number of radial branch channels leading to the surfaces of the guide member, so that the oil-carrying air operated by ⁇ said lubricating pump is delivered not only to the surfaces of said guide members contacting said rib member and the walls of said grooves, but also into the proper compressor casing wherein it thus also produces a lubricating as well as sealing oil film.
  • the combination of the balanced eccentric, Ion the one hand, and the lubricating and sealing oil ilrn permits to obtain a smooth operation of the compressor without a direct wearing contact of the compresssor pants and with an effective sealing elect between the suction side and the pressure side the same economic compression in one stage as achieved in the known compressors using a reciprocating piston.
  • the -oil lm which according to the invention is not only continuously renewed, but is also maintained under certain pressure, constitutes a distancing means between the displacer and the walls of the compressor casing with the advantageous result that the improved compressor complies with the desired requirements of high antifrictional quality, of a minimum rate of Wear and tear and of a maximum efficiency and output.
  • the present invention further proposes the provision of additional oil spray ducts in form of straight longitudinal grooves in the end surfaces of the rib member of -the displacer and in form of annular grooves in the end surfaces of the cylindrical displacer, these annular grooves being in communication with said straight grooves.
  • the end walls of said rib member and of the displacer are directly included in .the oil spray distribution system.
  • the said compression chamber formed by the recess of the compressor casing may Ibe connected by way of channels with the said grooves in the end surfaces of the rib member which in turn as stated are in direct communication with the said annular grooves in lthe end surfaces of .the displacer.
  • the arrangement may also be such that the said grooves in the end surfaces of the rib member are in direct communication with the said compression chamber.
  • the arrangement may be such that channels connecting the compression chamber with the grooves in the end surfaces of the rib member are provided in the walls of the compressor casing or alternatively in the rib member itself. In this lat-ter case these channels in the rib member are conveniently in direct communication with the grooves in the end surfaces of the rib member and ⁇ by way of these grooves with the annular grooves in the end walls of the displacer.
  • the intake opening of the compression cham-ber of the lubricating pump is provided with a nonreturn valve; a like valve may be provided between said chamber and the oil spray distribution system.
  • the oil container instead of being arranged in the base or support of the compressor, may also be dispos-ed at any other place, for instance, near the cornpression 'chamber of the lubricating pump eg. in fthe end walls of the compressor casing.
  • the wick or wicks of the oil container or containers may be elongated up to a level of the said compression charnber so as to advantageously shorten the circuit of the oilcarrying lair current.
  • An important feature of the invention consists in that the rib member and the compression chamber are of such dimensions that the oil spray is injected into the dlstribution system under certain pressure capable of mamtaining the oil film as a distancing means between the displacer and the compressor casing.
  • FIG. 1 a schematic cross sectional view of the improved rotary compressor according to the invention
  • FIG. 2 a schematic sectional view of the displacer, bearings and eccentric on a plane perpendicular to that of FIG. 1;
  • FIG. 3 a front view of the lcompressor according to FIGURES 1 and 2 Without the respective end wall;
  • FIG. 4 a longitudinal sectional view of the compressor according to FIG. 3;
  • FIG. 5 a cross sectional view of a modified embodiment of the compressor according to the invention.
  • FIG. 6 a longitudinal sectional View on a plane perpendicular to that of FIG. 5, and
  • FIG. 7 a fragmentary cross sectional view of a further modified embodiment of the compressor according to the invention.
  • the rotary compressor comprises a cylindrical casing 1 with a central driving shaft 2 rotatively mounted in the end walls 31 (FIG. 4) of said casing.
  • An eccentric 3 is fixed to the shaft 2 and carries the bearings 5 which in turn carry the cylindrical displacer 8.
  • the eccentric 3 in its portion of larger extension-with regard to the shaft 2- is provided with cavities 4 for reducing .the weight of this eccentric portion.
  • the eccentric between its end portions which carry the bearings 5 forms an intermedate annular cavity 6.
  • a flywheel mass 7 is fixed to the driving shaft 2 as shown in FIG.
  • the displacer 8 is conveniently provided with a corresponding recess as indicated at 9.
  • the displacer 8 is provided at least at one end with an annular cavity of a diameter corresponding to that of the recess 9, which is engaged and filled conveniently by a corresponding annular projection 10 of the respective end wall of the compressor casing.
  • the displacer 8 is provided as usually with ⁇ a radially projecting rib member 11 extending into a recess of the casing 1 and separating the suction side from the pressure side of the compressor i.e. the intake opening 13 from the outlet opening 14.
  • the outlet opening 14 comprises a nonreturn valve 32 (FIG. 4).
  • the intake opening 13 is conveniently provided with an air filter 33.
  • the said recess of the casing 1 forms near the inner wall of the latter a pair of opposite semi-cylindrical grooves for containing a pair of correspondingly shaped guide members 12 between which the guide members 11 slides in reciprocating motion and acts as a pump piston in a compression chamber 19 formed in an extension of the casing 1 beyond said semi-cylindrical grooves.
  • Each of the guide mem-bers is provided with a central longitudinal bore 18 and with a number of branch channels 21 leading from said bore to the outer surfaces of the guide members 12.
  • the pump constituted by the rib member 11 as a pump piston and by the recess 19 as a compression chamber, according to the invention is provided with an improved distribution system for the oil-carrying air or oil spray supplied by said pump.
  • This distribution system in the first instance comprises the above-mentioned bores 18 with their branch channels 21 in the guide members 12.
  • the rib member in its downward movement by way of the intake duct 34 (FIG. 4) sucks air into the compression chamber 19 and in its upward movement delivers the air by way of a duct 15 conveniently provided with a nonreturn valve 20 (FIG. 1) to a duct 16.
  • This duct 16 may be a bore in the casing 1 which as shown in FIG.
  • a wick 17 provided in an oil container 21 projects into said duct 16 and continuously delivers lubricating oil to the air current produced by said pump and circulated through the ducts 15, 16, 161 and to be injected into said bores 18 and branch channels 21.
  • the arrangement of these branch channels is such that the major part of the oil spray is supplied to the surfaces of the guide members 12 contacting the side walls of the rib member 11. As this rib member slides up and down, certain part of the oil spray enters the compressor and the rest is delivered to the outer surfaces of the guide members 12.
  • this 4oil film has not only a perfect lubricating and sealing effect of the rib member which separates the suction side from the pressure side of the compressor with the result that its efficiency is increased, -but also acts as a distance means between the surfaces of the displacer and th-e inner walls of the compressor casing which assists in avoiding wear and tear and in prolongatinig the lifetime of the compressor.
  • As practice has tought the oil spray even reaches the bearings 5 and takes charge of its permanent lubrication.
  • the compression chamber 19 by way of a nonreturn valve 20 may be directly connected with the atmosphere or as shown in FIG. 5 by means of Va duct 34 with the air lter 33 of the compressor.
  • the end surfaces of the rib member 11 are provided with straight longitudinal grooves 22 which are in direct communication with annular grooves 23 (FIG- URES 5 and 6) cut into the end surfaces of the gyriatory displacer 8.
  • the compression chamber 19 is in communication by way of the nonreturn valve 20 with a cross channel 35 which in turn com# municates with a pair of ducts 24 and 25 provided in the walls of the compressor casing.
  • These ducts 24 and 25 establish the connection with the straight grooves 22 in the end surfaces of the ri-b member 11 and by way of branch channels as indicated at 36 with the longitudinal bores 18 of the guide members 12.
  • the nonreturn valve 20 be-ing so arranged that by the downward stroke of the rib member 11 air is sucked in by way of the air intake 34 and not by way of the channnel 35 and ducts 24, 25.
  • the air intake 34 may be connected as shown in FIG. 5 with the air filter of the compressor or with the atmosphere as shown in FIG. 7.
  • an oil container may be iarranged in each of the end walls of the compressor casing with the advantageous result that the oil spray current produced by the pump 11, 19 is shortened.
  • the Wicks 17 may be dispensed with and the ducts 24, 25 may be in communication by way of suitable nozzles with the respective oil containers provided in the end walls of the compressor casing.
  • FIG. 6 Another embodiment has been simultaneously shown in FIG. 6, comprising a pair of channels 26 in the rib member 11 and connecting the compression chamber 19 by way of the nonreturn valve 27 with the straight longitudinal grooves 22 in the end surfaces of the rib member 11.
  • the valve 27 is destined for preventing the oil spray from being sucked back through the channels 26 into the compression chamber 19.
  • the oil lrn under pressure is really capable of providing a distance means.
  • said guide members 12 as well -as the rib member 11 are also provided with a lubricating and sealing oil film which is permanently renewed and maintained under pressure.
  • the oil spray which reaches the interior of the compressor is quantitatively so small as compared the quantity of :air which the compressor sucks in by way of the filter 33 and pushes out by way of the outlet 14 that a contamination of the compressed air does not occur.
  • the grooves 22 in the end surfaces of the rib member 11 reach the upper end of the latter and thus are in direct communication with the compression chamber 19.
  • the grooves 22 of the end walls of the compressor casing are in communication with the annular grooves 23 of the displacer 8.
  • the compression chamber 19 has an air intake 34 provided with a nonreturn valve 20 and connected with the atmosphere or with the oil filter of the compressor.
  • the wick projects directly into the intake 34, whereby the construction of the compressor is simplified, particularly if the oil container is arranged somewhere adjacent the extension of the casing 1 which forms the recess for the rib member 11 and the compression chamber 19.
  • a rotary compressor comprising a cylindrical casing, a central driving shaft rotatively mounted in .the end walls of said casing, an eccentric fixed .on said shaft in said casing, at least one cavity formed in said eccentric in its portion of iliarger extension, bearing means arranged on said eccentric efor a cylindrical displacer, at least one annular cavity formed by said eccentric, and witlhin said displacer a flywheel mass on said shaft in a portion of said annular cavity diametrically opposite said first-mentioned cavity for substantially balancing said portion of larger extension ⁇ of the eccentric, a rib memlber radially projecting from said displacer into a recess provided in said casing, this recess forming near .the inner Wall of said casing a pair of opposite semi-cylindrical grooves for containing corresponding rotary guide members between Which said rib member projects into a compression chamber formed by said recess -beyond said grooves, said rib memlber acting as
  • a rotary compresso-r comprising a cylindrical casing, a centnal driving shaft rotatively mounted in the end walls of said casing, an eccentric fixed on said shaft in said casing, at least one cavity formed in said eccentric in its portion of langer extension, bearing means arranged -on said eccentric for a cylindrical displacer, an annular cavity formed by said eccentric at each end thereof and at each side of an intermediate portion of said eccentric carries said bearing means for said displacer, a flywheel mass provided on said shaft in a portion of each of said annular cavities diametrically opposite said first-mentioned cavity for substantially balancing said portion of larger extension of the eccentric, a rib member radially projecting from said displacer into .a recess provided in said casing, this recess forming near the inner Wall of said casing a pair of opposite semi-cylindrical grooves for containing corresponding rotary guide members between which said rib member projects int-o
  • a rotary compressor comprising la cylindrical casing, a central driving shaft rotatively mounted in the end walls of said casing, an eccentric fixed on said shaft in said casing, at least one cavity formed in said eccentric in its portion of larger extension, bearing means arranged on said eccentric for a cylindrical displacer, at least one annular cavity formed by said eccentric, and within said displacer a ywheel mass on said shaft in a portion of said annular cavity diametrically opposite said first-mentioned cavity and in a recess of said displacer in alignment with said annular cavity of said eccentric for substantially balancing said portion of larger extension of the eccentric, a rib member radially projecting from said displacer into a recess provided in said casing, this recess forming near the inner wall .of said casing a -pair of opposite semi-cylindrical grooves for containing corresponding rotary guide members between which said rib member projects into la compression chamlber formed by said recess 'beyond said grooves
  • a rotary compressor comprising a cylindrical casing, a central driving shaft rotatively mounted in the end walls of said casing, :an eccentric iiXed on said shaft in said casing, at least one cavity for-med in said eccentric in its portion of larger extension, bearing means arranged on said eccentric for a cylindrical displacer, an annular cavity formed by said eccentric at each end thereof and at each side of an intermediate portion of said eccentric which ca-rries said bearing means for said displacer, a flywheel mass provided on said shaft in a portion of each of said annular cavities diametrically opposite said rstmentioned cavity and in corresponding recesses of said displacerA in alignment with said annular cavities of said eccentric for balancing said por-tion of larger extension of said eccentric, a rib member radially projecting from said displacer into a recess provided in said casing, this recess forming near .the inner wall of said casing a pair of opposite semi-cylindrical grooves for containing corresponding
  • said rib member acting as a pump piston in said compression chamber, air conducting means connecting said compression chamber with an oil supply means and duct means from said oil supply means to an oil spray distribution system for producing a lubricating, sealing and distancing oil film under pressure between component parts of ythe compressor.
  • a rotary compressor comprising a cylindrical casing, a central driving shaft rotatively mounted in the end walls of said casing, an eccentric fixed on said shaft in said casing, at least one cavity rformed in said eccentric in its portion of larger extension, bearing means arranged on said eccentric for a cylindrical displacer, a-t least one annular cavity formed by said eccentric and Within said displacer a ywheel mass on said shaft in a portion of said annular cavity diametrically opposite said rstmentioned cavity for substantially balancing said portion of larger extension of the eccentric, a rib member projecting radially from said displacer into a recess provided in said casing, this recess forming near the inner wall of said casing a pair of opposite semi-cylindrical grooves for containing corresponding rotary guide members between which said rib member projects into a compression chamber formed 'by said recess beyond said grooves, said rib member acting as a pump piston in said compression chamber, an air duct provided with a non-
  • a rotary compressor as set forth in claim 6, wherein the said oil spray distribution system comprises additional oil spray ducts in form of straight longitudinal grooves in the end Isurfaces of the said rib member and in form of annular grooves in the end surfaces of the said displacer in direct communication with said straight grooves, and channels provided in the walls of the compressor casing connecting said straight grooves and thereby said annular grooves with the said compression chamber.
  • a rotary compressor as set forth in claim 6, wherein the said oil spray distribution system comprises additional oil spray ducts in form of straight longitudinal grooves in the end surfaces of the said rib member and in direct communication therewith annular grooves in the end surfaces of the said displacer, and a pair of channels in said rib member connecting said straight longitudinal grooves with the said compression chamber with the interposi-tion of a nonreturn valve.
  • a rotary compressor as set forth in claim 6, wherein the said oil spray distribution system comprises additional oil spray ducts in form of straight longitudinal grooves in the end walls of the said rib member and in direct communication Atherewith annular grooves in the end surfaces of the said displacer, channels provided in the walls of the compressor casing connecting said straight grooves and thereby said annular grooves with the said compression chamber, and a pair of wicks extending from an oil container through corresponding channels in the end walls of the compressor casing into said first-mentioned channels which connect said straight grooves with said compression chamber.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
US437956A 1964-03-11 1965-03-08 Rotary compressor Expired - Lifetime US3269646A (en)

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DEJ0025422 1964-03-11

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US (1) US3269646A (de)
JP (1) JPS4216099B1 (de)
BE (1) BE660481A (de)
CH (2) CH434546A (de)
DE (1) DE1428140A1 (de)
GB (1) GB1033454A (de)
NL (1) NL6502780A (de)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3841802A (en) * 1972-03-10 1974-10-15 Gvang Motor Co Ltd Energy conversion device
DE2700522A1 (de) * 1977-01-07 1978-07-13 Borsig Gmbh Gekapselter rotationskolbenkompressor, insbesondere kaeltekompressor
US5105911A (en) * 1991-04-02 1992-04-21 Dresser Industries, Inc. Gas meter counter unit lubrication system
US5383774A (en) * 1992-04-28 1995-01-24 Daikin Industries, Ltd. Rotary compressor having blade integrated in roller
EP0652373A1 (de) * 1993-05-11 1995-05-10 Daikin Industries, Limited Drehkolbenverdichter
EP0683321A1 (de) * 1993-12-08 1995-11-22 Daikin Industries, Limited Schwingender rotations-kompressor
US5577903A (en) * 1993-12-08 1996-11-26 Daikin Industries, Ltd. Rotary compressor
US5616019A (en) * 1995-06-13 1997-04-01 Kabushiki Kaisha Toshiba Rolling piston type expansion machine
CN100427761C (zh) * 2004-01-22 2008-10-22 大金工业株式会社 摇动压缩机
US20090081064A1 (en) * 2007-09-26 2009-03-26 Kemp Gregory T Rotary compressor
US20110002803A1 (en) * 2008-03-11 2011-01-06 Daikin Industries, Ltd. Expander
JP2013139720A (ja) * 2011-12-28 2013-07-18 Daikin Industries Ltd 回転式圧縮機
RU2620465C1 (ru) * 2016-06-14 2017-05-25 Петр Андреевич Семчук Роторный насос
US10012081B2 (en) 2015-09-14 2018-07-03 Torad Engineering Llc Multi-vane impeller device

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3521981A (en) * 1968-08-30 1970-07-28 Edward Krzyszczuk Pump or compressor
GB2402975A (en) * 2003-06-18 2004-12-22 Carmeli Adahan Rotary single vane pump with simplified vane-and-socket joint
JP4958534B2 (ja) * 2006-12-21 2012-06-20 サンデン株式会社 スクロール圧縮機

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1616913A (en) * 1925-12-14 1927-02-08 Climax Engineering Co Force-feed lubrication from compressor blade
US1633056A (en) * 1925-01-23 1927-06-21 Climax Engineering Co Rotary-compressor refrigerating machine
FR725051A (fr) * 1930-11-20 1932-05-07 Escher Wyss & Cie Const Mec Compresseur à piston excentré à mouvement circulaire
US1890574A (en) * 1930-05-12 1932-12-13 Central Scientific Co Vacuum pump
FR805929A (fr) * 1935-05-09 1936-12-03 Rotorkompressoren A G Pompe pour fluides liquides ou gazeux
GB484040A (en) * 1936-06-03 1938-04-29 Alessandro Tebaldi Improved means for controlling the fluid outlet in rotary compressors
US2422972A (en) * 1944-05-26 1947-06-24 Frank W Knowles Winged-strap rotary compressor
US2995292A (en) * 1957-11-20 1961-08-08 Specialties Dev Corp Pressure intensifier
US3116012A (en) * 1962-04-03 1963-12-31 August Pablo Machine capable of operating as compressor and pump

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1633056A (en) * 1925-01-23 1927-06-21 Climax Engineering Co Rotary-compressor refrigerating machine
US1616913A (en) * 1925-12-14 1927-02-08 Climax Engineering Co Force-feed lubrication from compressor blade
US1890574A (en) * 1930-05-12 1932-12-13 Central Scientific Co Vacuum pump
FR725051A (fr) * 1930-11-20 1932-05-07 Escher Wyss & Cie Const Mec Compresseur à piston excentré à mouvement circulaire
FR805929A (fr) * 1935-05-09 1936-12-03 Rotorkompressoren A G Pompe pour fluides liquides ou gazeux
GB484040A (en) * 1936-06-03 1938-04-29 Alessandro Tebaldi Improved means for controlling the fluid outlet in rotary compressors
US2422972A (en) * 1944-05-26 1947-06-24 Frank W Knowles Winged-strap rotary compressor
US2995292A (en) * 1957-11-20 1961-08-08 Specialties Dev Corp Pressure intensifier
US3116012A (en) * 1962-04-03 1963-12-31 August Pablo Machine capable of operating as compressor and pump

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3841802A (en) * 1972-03-10 1974-10-15 Gvang Motor Co Ltd Energy conversion device
DE2700522A1 (de) * 1977-01-07 1978-07-13 Borsig Gmbh Gekapselter rotationskolbenkompressor, insbesondere kaeltekompressor
US5105911A (en) * 1991-04-02 1992-04-21 Dresser Industries, Inc. Gas meter counter unit lubrication system
US5383774A (en) * 1992-04-28 1995-01-24 Daikin Industries, Ltd. Rotary compressor having blade integrated in roller
EP0652373A1 (de) * 1993-05-11 1995-05-10 Daikin Industries, Limited Drehkolbenverdichter
EP0652373A4 (de) * 1993-05-11 1995-12-13 Daikin Ind Ltd Drehkolbenverdichter.
US5564916A (en) * 1993-05-11 1996-10-15 Daikin Industries, Ltd. Rotary compressor having strengthened partition and shaped recesses for receiving the strengthened partition
EP0683321A1 (de) * 1993-12-08 1995-11-22 Daikin Industries, Limited Schwingender rotations-kompressor
EP0683321A4 (de) * 1993-12-08 1996-05-15 Daikin Ind Ltd Schwingender rotations-kompressor.
US5577903A (en) * 1993-12-08 1996-11-26 Daikin Industries, Ltd. Rotary compressor
US5616019A (en) * 1995-06-13 1997-04-01 Kabushiki Kaisha Toshiba Rolling piston type expansion machine
CN100427761C (zh) * 2004-01-22 2008-10-22 大金工业株式会社 摇动压缩机
US20090081064A1 (en) * 2007-09-26 2009-03-26 Kemp Gregory T Rotary compressor
US20090081063A1 (en) * 2007-09-26 2009-03-26 Kemp Gregory T Rotary fluid-displacement assembly
US8113805B2 (en) 2007-09-26 2012-02-14 Torad Engineering, Llc Rotary fluid-displacement assembly
US8177536B2 (en) 2007-09-26 2012-05-15 Kemp Gregory T Rotary compressor having gate axially movable with respect to rotor
US8807975B2 (en) 2007-09-26 2014-08-19 Torad Engineering, Llc Rotary compressor having gate axially movable with respect to rotor
US20110002803A1 (en) * 2008-03-11 2011-01-06 Daikin Industries, Ltd. Expander
JP2013139720A (ja) * 2011-12-28 2013-07-18 Daikin Industries Ltd 回転式圧縮機
US10012081B2 (en) 2015-09-14 2018-07-03 Torad Engineering Llc Multi-vane impeller device
RU2620465C1 (ru) * 2016-06-14 2017-05-25 Петр Андреевич Семчук Роторный насос

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Publication number Publication date
CH434546A (de) 1967-04-30
NL6502780A (de) 1965-09-13
JPS4216099B1 (de) 1967-09-02
GB1033454A (en) 1966-06-22
CH464429A (de) 1968-10-31
DE1428140A1 (de) 1969-11-20
BE660481A (de) 1965-07-01

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