US3820923A - Single stage or multistage rotary compressor - Google Patents

Single stage or multistage rotary compressor Download PDF

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Publication number
US3820923A
US3820923A US00301558A US30155872A US3820923A US 3820923 A US3820923 A US 3820923A US 00301558 A US00301558 A US 00301558A US 30155872 A US30155872 A US 30155872A US 3820923 A US3820923 A US 3820923A
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Prior art keywords
compression
housing
rotary compressor
fluid
rotary
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US00301558A
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English (en)
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A Zweifel
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AIRFINA Ets
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AIRFINA Ets
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Priority claimed from CH1750871A external-priority patent/CH557958A/de
Priority claimed from CH1018272A external-priority patent/CH564153A5/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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S418/00—Rotary expansible chamber devices
    • Y10S418/01—Non-working fluid separation

Definitions

  • the number of cooling medium inlet nozzles are over 20 per compression path, the ratio of length to width of a nozzle orifice exceeds 10, its minimum width is less than 0.1 V7, where F denotes the sum of the cross-sectional areas of the nozzles.
  • PATENTEUJUH28 I874 sum as or 11 l l g:
  • PATENTEDMZB 1914 saw us er w PAIENTEDaunza um sum "10 or 11 SINGLE-STAGE OR MULTISTAGE ROTARY COMPRESSOR
  • the present invention concerns a single-stage or multi-stage rotary compressor with injection of coolants into the compression chamber.
  • Rotary compressors in the form of sliding-vane compressors and screw-compressors are known where oil or any other liquid is injected into the compression chamber to cool the compression medium. Thorough tests have shown that their efficiency can be improved without major manufacturing costs.
  • the present invention is characterized in that the number of injection nozzles for the coolant is over 20 per compression stage, and/or, if the ratio of length to width of a nozzle orifice exceeds 10, its minimum width is less than 0.1 F, where F is the sum of the injection surfaces of all nozzles per compression stage.
  • Air is assumed here as a compression medium and oil as the injected liquid, but all consideration can also be extended to other compression media and cooling liquids.
  • FIGJI shows a schematic representation of the construction of a rotary sliding-vane compressor with oil separation system in 'a section along the line [-1 of FIG. 3.
  • FIGS. 2, 2a, 2b, 2c, 2d show portions of the rotary sliding-vane compressor according to FIG. 1 with cylinder, rotor, oil injection system and combined regulating valve along the line IIII of FIG. 3 and in a perspective,
  • FIG. 3 shows a longitudinal section through the portion of the rotary sliding-vane compressor along the line III-III of FIG. 2.
  • FIG. 4 shows a schematic representation of the construction of a screw compressor with oil separation system in a section along the line IV-IV of FIG. 7.
  • FIG. 5 shows adiagram of a rotary compressor in accordance with the ISO specifications, according to FIGS. I and 4 represented both for no-load and fullload.
  • FIGS. 6 and 60 view portions of the screw compressor according to FIG. 4 with cylinder male rotor, female rotor, oilinjection system (in FIGS. 6 and 60 only the injection nozzles for the male rotor are shown) and combined regulating valve along the line VVI of FIG. 9.
  • FIG. 7 shows a longitudinal section through the portion of the screw compressor along the line VII-VII of FIG. 6.
  • FIGS. 8, 80 show a development of the rotor surface of the screw compressor for two rotor positions. In these developments the location for intake, compression, the oil injection and the air delivery are visible.
  • FIG. 8 shows the smallest cell volume 11 into which coolant is still injected
  • FIG. 8a the smallest closed cell volume 11
  • FIG. 9 shows a top view of the screw compressor according to FIG. 6 with suction flange and oil pump.
  • FIG. 10 shows a view of the screw compressor according to FIG. 6 from the rear, with injection flange, outlet and axial oil supply feeding.
  • a lowercasing 1 is assembled with an upper casing 3'.
  • FIGS. 6, 6a, 6b, 6c, 6d show, partly in perspective I Connected to the casing 1, 3 is a cylinder 5 with the axis 6.
  • a rotor 8 is mounted with its axis 9 eccentrically to the cylinder axis 6.
  • the cylinder 5 is provided with one or several air intake ports 11 as well as a number of air outlet ports 12.
  • the rotor 8 has substantially radially arranged sliding vanes 14 which hug the inner surface of the cylinder 5, due to the centrifugal force of the revolving rotor 8.
  • a lower casing 1 is assembled with an upper casing 3.
  • Connected to the casings l, 3 is a double cylinder with the axes 106 and 107.
  • a first filter disk 16 with a relatively large filter surface for example, felt
  • This filter 18 is joined, in the direction of the air flow, by a second filter disk whose surface is subdivided into an outer annular part 20 and into an inner annular part 21.
  • the corresponding oil pits 17 and 19 resp. are likewsie visible.
  • a wire gauze filter 22 After the outerannular part 20 is situated a wire gauze filter 22, after which the inner annular part 21 of the second disk is passed, and subsequently the delivery duct 24, the non-return valve 25 and the air connection 26.
  • the oil pits l5, l7 and 19 are connected with the suction chamber of the compressor by an oil recover pipe 43 (FIGS. 3, 5).
  • the oil air mixture delivered by the compressor arrives in the lower casing l-, in which the oil deposits at the bottom, while the compressed air flows upward and is cleaned in the filters 16, 18, 20-, 22 and 21 which follow. Subsequently the air flows through the non-return valve 25 which preceeds an air cooler 28 (FIG. 5).
  • the oil flows into an oil cooler 27 (schematically represented in FIG. 5) to be cooled and then flows into intake 48 of a combined regulating valve 33.
  • the oil then enters pre-chamber 52 where it is distribured through nozzles 54, 55 (bores or slots) and into the compression chamber.
  • the intake air or the intake gas flows over the combined multiple function-regulating valve 33 into a suction chamber 32.
  • the combined regulating valve 33 which regulates ON/OFF (principally it could also be regulated continuously by throttling the volume of air admitted and in screw compressors also by means of bypassing air inside the cylinder), also comprises a valve head 35 with a valve shaft 36. Its free end is connected to a control piston 38 in a control cylinder 37. The free end of the control cylinder 37 carries a connection 40 for the pressure medium (normally compressed air).
  • the pressure medium normally compressed air
  • control piston 38 is embodied an insert 42.
  • the supply of the cooling oil to be injected into the compression chamber is effected from the lower casing 1 designed as an oil tank, which is under the final compression pressure, and from which oil is taken through a line and the cooler 27 (FIG.
  • a pump 86 may be provided in order to increase the oil pressure.
  • the oil flows subsequently into a chamber 48 (FIGS. 2 and 6) and from there through a valve seat 50 into an oil pre-chamber 52.
  • One end of the control piston 38 is designed as a valve body which controls the passage between the chamber 48 and the oil pre-chamber 52.
  • the air temperature will be correspondingly high there and cannot be determined by measuring the temperature at the outlet, because here liquid and air mix again so that the air temperature will be substantially lower than in the compression chamber. Furthermore the temperature measurement here represents the oil rather than the air temperature. Even with injection at higher air pressures, the obtained mixing of cooling liquid and air is rather poor, as long asthe liquid is not injected through many evenly distributed nozzles or through one or several thin slots. It required extensive research to find what advantages a uniformly distributed injection offers, particularly in the range of higher air pressures and air temperatures.
  • the known cooling system is also less effective in the sense that in some models because of premature aging the cooling oil must be changed after arelatively modcorresponding division into many individual nozzles,
  • the cooling oil can be excellently distributed in the compression chamber in a finely atomized state.
  • the degree of atomization By impingement of the oil jets or spray (or in the case of injection through slots, of the oil curtains) on the rotor surface, the degree of atomization, and thus the distribution of the cooling liquid into the air tobe cooled can be improved.
  • the air/oil mixture is also microscopically more homogeneous.
  • the uniform distribution of the oil prevents leakage at most points. This improves not only the efficiency, but also the oil separation.
  • cell volume we understand the volume of the enclosed space (cell) in which the air is contained during the compression.
  • a cell volume as described below can also be defined after the outlet ports have been reached.
  • the cell volume is defined by the opposing faces of two successive blades or sliding-vanes and by the respective surface of the rotor and of the cylinder, considered as closed (FIG. 2).
  • the cell volume is defined by the end wall and cylinder wall on the pressure side, considered as closed, and by the tooth flanks.
  • the end wall 170 on the suction side is interrupted by the intake 11, the end wall on the pressure side 169 by the outlet port 12.
  • the complicated boundary 120 of the cell volume by the meshing of the teeth of the male rotor and of the female rotor is represented schematically in FIGS. 8 and 8a.
  • V The smallest cell volume into which coolant is still injected
  • V the smallest closed cell volume at which the cell reaches the first edge of an oil pocket or the first edge of an air outlet port (if there is no corresponding pocket provided)
  • V corresponds to the hatched area CDEF
  • V corresponds to the area GHIK.
  • V corresponds to the area ABCDEFGl-I
  • V to the area IKLMOPQR.
  • the air outlet ports 12 are connected by a duct 59 with the lower casing 1, from which an air duct 60 leads to the filters 16, 18, 20, 21 and 22.
  • the plate-shaped filters 16, 20, 21 are held on two tie rods 61, 62 and 161, 162 respectively which bear on the covers 64, 65, the tie rods being braced by means of nuts 63.
  • the lateral covering of the cylinder 5 and of the rotor 8 is effected in the rotary slidingvane compressor by means of two two-part cylinder covers 69, 70 which serve to receive the bearings 72, 73.
  • each cover 69, 70 is also arranged a stuffing-box ring 75, 76 which prevent outside air from getting into the bearings.
  • Leakage air charged with oil mist flows through slots 77 between spacer rings 80 and the covers 69, 70 into the bearings 72, 73 which are thus lubricated.
  • the leakage air then flows through ducts 74 into the suction side of the compressor.
  • the rotor shaft ends are designated with 78 and 79.
  • On one free end of the rotor shaft 79 is attached in the air-cooled model a cooling fan 81.
  • Pressure oil ducts 82 lead from the oil pre-chamber 52 into the covers 69, 70.
  • Lubricating and cooling oil is fed through ducts laterally to the rotor end faces as sealing liquid.
  • the lateral covering of the cyinder is effected in the screw compressors by means of two cylinder covers 169, which serve to receive the bearings 172, 173.
  • cover 169 In the cover 169 are also arranged two stuffing-box rings 175, 176 which prevent outside air from getting into the bearings. Leakage air containing oil mists flows through an annular slot 177 into the roller bearings 172 and 173 and from there through the bores 174 into the suction duct of the compressor.
  • Two control gear wheels 85 as well as an injection pump 86 can be arranged on the rotor shaft ends 179 and 183 preferably on the side opposite the drive. In the air-cooled model, this arrangement also includes a cooling propeller 81.
  • Pressure oil ducts 188 lead from the oil pre-chamber 52 into the cylinder-covers 169, 170'which supply cooling oil as sealing liquid through bores 182 laterally to the rotor end faces, so that the axial thrust of the rotor is at the same time partly compensated. Furthermore the oil ducts 184 are fed from the oil pre-chamber 52 and an axial injection from the end face on the pressure side is achieved through the nozzles 54. To this end it is of advantage to inject the cooling liquid only into the cell region limited by radial injection.
  • valve 33 described above and represented in detail in FIGS. 2 and 6 is new in its design. It is a combination valve with coaxially arranged valve bodies which are connected with each other mechanically, either rigidly or elastically. It is actuated by a control medium, here compressed air, which acts only on one side of a piston. In the present case it performs the following functions:
  • the resulting oil spray or jets strike against the rotating rotor 8 where they atomize.
  • the oil-air mixture as well as a swell of oil deposited on the bearing surface 7 of the cylinder 5 are pushed by the corresponding slidingvane 14 toward the pockets 58 and the air outlet ports namely during the time. in which the sliding-vane 14 passes by the outlet ports 12.
  • the oil pocket 58 as well as several air outlet ports 12 are provided. There is thus sufficient volume available into which the liquid .can escape when asliding-vane 14 passes by, so thatv jerky ejections are avoided.
  • a pressure switch 89 switches into the open position, a solenoid valve 91 feeds the control liquid and brings a servo-controlled slide-valve 92 into its noload position Lp
  • the tap line-connected between the two filters 20 and 21 is connected over the servo controlled slide-valve 92 with the outside ,air, so that the air blows off through this line.
  • the system pressure is unchanged (since the latter is higher than the dropping pressure in the lowercasing g 1 (FIGS. 1 and 4), the non-return'valve 25 closes), so
  • the pressure switchi89 trips (FIG. 5), causing the solenoid valve 91 to takeup the position VJ? With the valve in that position, no further control medium'reaches the servo-controlled valve 92 or the piston 38,"so that the combined control valve opens under the suction prevailing in the'chamber 32 (FIGS. 2 and 6).
  • the compressor begins to deliver, the pressure in the system system reaches that in the consumer system, the nonreturn valve 25 opens.
  • the valve 93 shuts down against the consumer system, thus preventing any bypassing of the third filter 21 by the valve 93.
  • the compressor delivers airto the charging system, i.e., to the air vessel, until this system also is completely charged. Then the compressor automatically switches to its idling position, as explained.
  • a rotary compressor with injection of the cooling medium into a compression chamber including in combination:
  • fluid inlet means coupled to said housing and communicating with the compression chamber; fluid outlet means spaced from said fluid inlet means an disposed through said housing so as to communicate with the compression chamber;
  • rotary compression means journaled in said housing and adapted to compress the fluid along a compression path, the compression path including the area between the interior periphery of said housing and the external periphery of said rotary compression means as the latter mentioned means rotates from said fluid inlet means to said fluid outlet means;
  • the compression path defining a cell of varying and decreasing volume between said fluid inlet and outlet means wherein the smallest cell volume v into which the cooling medium is still being injected, and the smallest close cell volume v of the compressor exhibits the relation:
  • a rotary compressor with injection of the cooling medium into a compressor chamber including in com bination:
  • fluid inlet means coupled to said housing and communicating with the compression chamber
  • fluid outlet means spaced from said fluid inlet means and disposed through said housing so as to communicate with the compression chamber; rotary compression means journaled in said housing and adapted to compress the fluid along a compres-.
  • the compression path including the area between the interior periphery of said housing and the external periphery of said rotary compression means as the latter mentioned means rotates from said fluid inlet means to said fluid outlet means;
  • a plurality of injection nozzles placed along the compression path so as to communicate with the compression chamber and adapted to inject the cooling medium therein, said compression path defining a cell of varying and decreasing volume between said fluid inlet and outlet means wherein the smallest cell volume v into which the cooling medium is still being injected, and the smallest close cell volume v of the compressor exhibits the relation:
  • a rotary compressor with injection of the cooling medium into a compression chamber including in combination:
  • fluid inlet means coupled to said housing and communicatingwith the compression chamber
  • rotary compression means journaled in said housing and adapted to compress the fluid along a compression path, the compression path including the area between the interior periphery of said housing and a portion of the external periphery of said rotary compression means as the latter mentioned means rotates from said fluid inlet means to said fluid outlet means;
  • the compression path defining a cell of varying and decreasing volume between said fluid inlet and outlet means wherein the smallest cell volume v into which the cooling medium is still being injected, and the smallest closed cell volume v of the compressor exhibits the relation:
  • each orifice has a substantially circular profile and has a diameter ranging from approximately 0.3 to 1.2 mm.
  • said housing is substantially cylindrically shaped and includes two substantially parallel opposed end walls, each of the end walls including a plurality of openings adapted to supply oil thereat to act as'a sealing and lubricating fluid for the ends of said rotary compression means positioned adjacent thereto.
  • said rotary compression means further includes bearing means positioned in each of the end walls for rotatably journaling the former mentioned means, and aperture means disposed through the end walls and adapted to communicate with and tap a portion of the compressed fluid and direct same to lubricate said bearing means,
  • said aperture means further including ducts to egress said portion of the compress fluid in an area adjacent said fluid inlet means.
  • the rotary compressor as in claim 5 further including an output path coupled to said fluid outlet means and guiding the compressed fluid therefrom, said output path further including filter means interposed therealong to filter the compressed fluid as it transverses therethrough.
  • said filter means comprises a filter plate, a filter housing dividing said filter plate into an included inner part and an outer part, the latter part defined around the inner part, said housing including baffles to direct the compressed fluid therethrough so that said filter plate experiences the compressed fluid flow in opposed directions.
  • said fluid outlet means comprises a plurality of outlet ports positioned on the interior periphery of said housing so 12 as to be substantially parallel to the longitudinal axis thereof.
  • each of said plurality of outlet ports communicates with a recess having a larger cross-sectional area then its respective one of each of said plurality of outlet ports, each of said recess being defined on the interior peripheral wall of said housing and adapted to facilitate the egress of oil and to facilitate isolation of said fluid inlet means from the compression chamber.
  • said filter means includes a first filter serially interposed along the the output path and a second filter positioned further along the output path and parallel spaced from said first filter, each of said first and second filters being substantially disc-shaped.
  • the rotary compressor as in claim 19 further including a wire gauge filter interposed between said first and second filters and adapted to filter the cooling medium suspended in the compressed fluid as it transverses therethrough.
  • said second filter includes a filter housing that divides said second filter into an included inner annular part and an outer annular part, the latter part disposed around and including the inner part, said housing directing the compressed fluid serially through the outer annular part and then through the inner annular part, the outer annular pary having a surface area 1.5 times greater than the surface area of the inner annular part.
  • control piston includes a substantially hollow enclosed piston skirt, aperture means disposed through the walls of said piston skirt, ring-valve means adapted to ride within said piston skirt and spring means biasing said ring-valve means so that when said piston skirt abuts against said valve seat to block the flow of cooling medium to said pre-chamber, said spring means lifts said ring-valve means from said piston skirt allowing a portion of the cooling medium to flow therearound to egress said aperture means into said pre-chamber and flow through said plurality of nozzles thereby lubricating and cooling said rotary compression means.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary-Type Compressors (AREA)
  • Fluid-Pressure Circuits (AREA)
US00301558A 1971-12-01 1972-10-27 Single stage or multistage rotary compressor Expired - Lifetime US3820923A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1750871A CH557958A (de) 1971-12-01 1971-12-01 Ein- oder mehrstufiger rotationskompressor.
CH1018272A CH564153A5 (enrdf_load_stackoverflow) 1972-07-07 1972-07-07

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US00301558A Expired - Lifetime US3820923A (en) 1971-12-01 1972-10-27 Single stage or multistage rotary compressor

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US (1) US3820923A (enrdf_load_stackoverflow)
JP (1) JPS5653112B2 (enrdf_load_stackoverflow)
CA (1) CA962645A (enrdf_load_stackoverflow)
DE (1) DE2240018C3 (enrdf_load_stackoverflow)
ES (1) ES409115A1 (enrdf_load_stackoverflow)
FR (1) FR2164224A5 (enrdf_load_stackoverflow)
GB (1) GB1402435A (enrdf_load_stackoverflow)

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US4080119A (en) * 1974-06-24 1978-03-21 Sven Evald Eriksson Method and device for draining oil from the gear case of a compressor
US4174196A (en) * 1976-07-28 1979-11-13 Hitachi, Ltd. Screw fluid machine
US4295806A (en) * 1978-05-26 1981-10-20 Mitsubishi Denki Kabushiki Kaisha Rotary compressor with wire gauze lubricant separator
US4341506A (en) * 1979-08-14 1982-07-27 Gutehoffnungshutte Sterkrade A.G. Apparatus for the generation of compressed air
US4420293A (en) * 1979-09-24 1983-12-13 Isartaler Schraubenkompressoren Gmbh Liquid cooled compressor with improved liquid separation
US4439121A (en) * 1982-03-02 1984-03-27 Dunham-Bush, Inc. Self-cleaning single loop mist type lubrication system for screw compressors
US4563138A (en) * 1981-12-11 1986-01-07 Isartaler Schraubenkompressoren Gmbh Compressor system with oil separation
US4657487A (en) * 1984-12-07 1987-04-14 Siemens Aktiengesellschaft Vacuum generating apparatus including liquid ring pump, pre-separator, two heat exchangers and fine separator
US4761123A (en) * 1987-06-11 1988-08-02 Ingersoll-Rand Company Lubrication arrangement, in an air compressor
GB2196696B (en) * 1986-10-22 1991-05-29 Utile Engineering Co Limited Pumps
WO1995018945A1 (en) * 1994-01-10 1995-07-13 Fresco Anthony N Cooling and sealing rotary screw compressors
US5653585A (en) * 1993-01-11 1997-08-05 Fresco; Anthony N. Apparatus and methods for cooling and sealing rotary helical screw compressors
US6183227B1 (en) * 1998-04-09 2001-02-06 Hitachi, Ltd. Screw compressor
US20030143095A1 (en) * 2002-01-25 2003-07-31 Hiromiki Ono Gas compressor
US20080152524A1 (en) * 2005-06-29 2008-06-26 Mayekawa Mfg. Co., Ltd. Oil supply method of two-stage screw compressor, two-stage screw compressor applying the method, and method of operating refrigerating machine having the compressor
WO2012030741A2 (en) 2010-08-30 2012-03-08 Oscomp Systems Inc. Compressor with liquid injection cooling
US8794941B2 (en) 2010-08-30 2014-08-05 Oscomp Systems Inc. Compressor with liquid injection cooling
US9267504B2 (en) 2010-08-30 2016-02-23 Hicor Technologies, Inc. Compressor with liquid injection cooling
WO2016160856A2 (en) 2015-03-30 2016-10-06 Hicor Technologies, Inc. Compressor with liquid injection cooling
WO2016181259A1 (en) * 2015-05-14 2016-11-17 Virgilio Mietto Improved volumetric screw compressor
US9920763B2 (en) 2015-09-17 2018-03-20 Ingersoll-Rand Company Contact cooled rotary airend injection spray insert
US20190101121A1 (en) * 2017-10-04 2019-04-04 Ingersoll-Rand Company Screw compressor with oil injection at multiple volume ratios
US10851786B2 (en) 2017-09-27 2020-12-01 Ingersoll-Rand Industrial U.S., Inc. Rotary screw compressor with atomized oil injection
US10975869B2 (en) 2017-12-13 2021-04-13 Exponential Technologies, Inc. Rotary fluid flow device
US11149734B2 (en) 2016-08-23 2021-10-19 Hitachi Industrial Equipment Systems Co., Ltd. Fluid machine
US11168683B2 (en) 2019-03-14 2021-11-09 Exponential Technologies, Inc. Pressure balancing system for a fluid pump
US11215182B2 (en) 2018-03-01 2022-01-04 Ingersoll-Rand Industrial U.S., Inc. Multi-stage compressor having interstage lubricant injection via an injection rod
US11231036B2 (en) 2017-09-04 2022-01-25 Hitachi Industrial Equipment Systems Co., Ltd. Screw compressor having an opening of a fluid supply portion between the compression intersection line and a trajectory line
US11346346B2 (en) * 2017-12-08 2022-05-31 Hitachi, Ltd. Liquid-cooled type compressor having first and second nozzle injection ports with different characteristics
US11713759B2 (en) * 2017-07-27 2023-08-01 Ing. Enea Mattei S.P.A. Vane compressor with an improved lubrication system

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JPS5430125B2 (enrdf_load_stackoverflow) * 1973-12-04 1979-09-28
JPS5631688U (enrdf_load_stackoverflow) * 1979-08-20 1981-03-27
DE2938557A1 (de) * 1979-09-24 1981-04-23 Isartaler Schraubenkompressoren Gmbh, 8192 Gertsried Verdichteranlage
DE3022277A1 (de) * 1980-06-13 1981-12-24 Isartaler Schraubenkompressoren GmbH, 8192 Geretsried Verdichter mit oeleinspritzung, insbesondere schraubenverdichter
GB2081383B (en) * 1980-07-31 1983-12-21 Hydrovane Compressor The Co Lt Rotary compressors
US4375156A (en) * 1980-10-03 1983-03-01 Dunham-Bush, Inc. Closed loop compressed gas system with oil mist lubricated screw compressor
US4441871A (en) * 1981-12-18 1984-04-10 Hydrovane Compressor Company Limited Rotary compressors with primary and secondary oil separation means
GB2119443A (en) * 1982-04-24 1983-11-16 Gen Eng Radcliffe 1979 An oil sealed pump
DE3512961A1 (de) * 1985-04-11 1986-10-16 Bauer Schraubenverdichter GmbH, 8190 Wolfratshausen Schraubenverdichter in kompaktausfuehrung
FR2603666B1 (fr) * 1986-09-10 1990-11-09 Zimmern Bernard Compresseur injecte a commutateur de liquide
US4861246A (en) * 1988-01-07 1989-08-29 Bernard Zimmern Injected compressor with liquid switch
DE4223315A1 (de) * 1991-07-30 1993-02-04 Mannesmann Ag Einspritzgekuehlter vielzellenverdichter
JP7072350B2 (ja) * 2017-05-24 2022-05-20 株式会社神戸製鋼所 油冷式圧縮機

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US4035114A (en) * 1974-09-02 1977-07-12 Hokuetsu Kogyo Co., Ltd. Method for reducing power consumption in a liquid-cooled rotary compressor by treating the liquid
US3990818A (en) * 1975-02-27 1976-11-09 Curtiss-Wright Corporation Lubrication system for rotary piston mechanisms
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US4295806A (en) * 1978-05-26 1981-10-20 Mitsubishi Denki Kabushiki Kaisha Rotary compressor with wire gauze lubricant separator
US4341506A (en) * 1979-08-14 1982-07-27 Gutehoffnungshutte Sterkrade A.G. Apparatus for the generation of compressed air
US4420293A (en) * 1979-09-24 1983-12-13 Isartaler Schraubenkompressoren Gmbh Liquid cooled compressor with improved liquid separation
US4563138A (en) * 1981-12-11 1986-01-07 Isartaler Schraubenkompressoren Gmbh Compressor system with oil separation
US4439121A (en) * 1982-03-02 1984-03-27 Dunham-Bush, Inc. Self-cleaning single loop mist type lubrication system for screw compressors
US4657487A (en) * 1984-12-07 1987-04-14 Siemens Aktiengesellschaft Vacuum generating apparatus including liquid ring pump, pre-separator, two heat exchangers and fine separator
GB2196696B (en) * 1986-10-22 1991-05-29 Utile Engineering Co Limited Pumps
US4761123A (en) * 1987-06-11 1988-08-02 Ingersoll-Rand Company Lubrication arrangement, in an air compressor
US5653585A (en) * 1993-01-11 1997-08-05 Fresco; Anthony N. Apparatus and methods for cooling and sealing rotary helical screw compressors
WO1995018945A1 (en) * 1994-01-10 1995-07-13 Fresco Anthony N Cooling and sealing rotary screw compressors
US6183227B1 (en) * 1998-04-09 2001-02-06 Hitachi, Ltd. Screw compressor
US6273693B2 (en) 1998-04-09 2001-08-14 Hitachi, Ltd. Screw compressor
US20030143095A1 (en) * 2002-01-25 2003-07-31 Hiromiki Ono Gas compressor
US6851940B2 (en) * 2002-01-25 2005-02-08 Seiko Instruments Inc. Gas compressor
US8277207B2 (en) 2005-06-29 2012-10-02 Mayekawa Mfg. Co., Ltd. Oil supply method of two-stage screw compressor, two-stage screw compressor applying the method, and method of operating refrigerating machine having the compressor
US20080152524A1 (en) * 2005-06-29 2008-06-26 Mayekawa Mfg. Co., Ltd. Oil supply method of two-stage screw compressor, two-stage screw compressor applying the method, and method of operating refrigerating machine having the compressor
US20100089078A1 (en) * 2005-06-29 2010-04-15 Mayekawa Mfg. Co., Ltd. Oil supply method of two-stage screw compressor, two-stage screw compressor applying the method, and method of operating refrigerating machine having the compressor
US7722346B2 (en) * 2005-06-29 2010-05-25 Mayekawa Mfg. Co., Ltd. Oil supply method of two-stage screw compressor, two-stage screw compressor applying the method, and method of operating refrigerating machine having the compressor
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US8794941B2 (en) 2010-08-30 2014-08-05 Oscomp Systems Inc. Compressor with liquid injection cooling
US9267504B2 (en) 2010-08-30 2016-02-23 Hicor Technologies, Inc. Compressor with liquid injection cooling
US20180106255A1 (en) * 2010-08-30 2018-04-19 Hicor Technologies, Inc. Compressor with liquid injection cooling
US10962012B2 (en) * 2010-08-30 2021-03-30 Hicor Technologies, Inc. Compressor with liquid injection cooling
US9719514B2 (en) 2010-08-30 2017-08-01 Hicor Technologies, Inc. Compressor
US9856878B2 (en) 2010-08-30 2018-01-02 Hicor Technologies, Inc. Compressor with liquid injection cooling
WO2016160856A2 (en) 2015-03-30 2016-10-06 Hicor Technologies, Inc. Compressor with liquid injection cooling
EP3978758A2 (en) 2015-03-30 2022-04-06 Hicor Technologies, Inc. Compressor with liquid injection cooling
CN107624149A (zh) * 2015-05-14 2018-01-23 维尔吉利奥·米耶托 改进的容积式螺杆压缩机
WO2016181259A1 (en) * 2015-05-14 2016-11-17 Virgilio Mietto Improved volumetric screw compressor
US9920763B2 (en) 2015-09-17 2018-03-20 Ingersoll-Rand Company Contact cooled rotary airend injection spray insert
US11149734B2 (en) 2016-08-23 2021-10-19 Hitachi Industrial Equipment Systems Co., Ltd. Fluid machine
US11713759B2 (en) * 2017-07-27 2023-08-01 Ing. Enea Mattei S.P.A. Vane compressor with an improved lubrication system
US11231036B2 (en) 2017-09-04 2022-01-25 Hitachi Industrial Equipment Systems Co., Ltd. Screw compressor having an opening of a fluid supply portion between the compression intersection line and a trajectory line
US10851786B2 (en) 2017-09-27 2020-12-01 Ingersoll-Rand Industrial U.S., Inc. Rotary screw compressor with atomized oil injection
CN114857004A (zh) * 2017-10-04 2022-08-05 英格索兰工业美国公司 具有以多个体积比的油喷射的螺杆式压缩机
US11732715B2 (en) 2017-10-04 2023-08-22 Ingersoll-Rand Industrial U.S., Inc. Screw compressor with oil injection at multiple volume ratios
US12117001B2 (en) 2017-10-04 2024-10-15 Ingersoll-Rand Industrial U.S., Inc. Screw compressor with oil injection at multiple volume ratios
US11118585B2 (en) 2017-10-04 2021-09-14 Ingersoll-Rand Industrial U.S., Inc. Screw compressor with oil injection at multiple volume ratios
CN114857004B (zh) * 2017-10-04 2024-09-27 英格索兰工业美国公司 具有以多个体积比的油喷射的螺杆式压缩机
US20190101121A1 (en) * 2017-10-04 2019-04-04 Ingersoll-Rand Company Screw compressor with oil injection at multiple volume ratios
CN109854502B (zh) * 2017-10-04 2022-07-12 英格索兰工业美国公司 具有以多个体积比的油喷射的螺杆式压缩机
CN109854502A (zh) * 2017-10-04 2019-06-07 英格索尔-兰德公司 具有以多个体积比的油喷射的螺杆式压缩机
US11346346B2 (en) * 2017-12-08 2022-05-31 Hitachi, Ltd. Liquid-cooled type compressor having first and second nozzle injection ports with different characteristics
US11614089B2 (en) 2017-12-13 2023-03-28 Exponential Technologies, Inc. Rotary fluid flow device
US10975869B2 (en) 2017-12-13 2021-04-13 Exponential Technologies, Inc. Rotary fluid flow device
US11781547B2 (en) 2018-03-01 2023-10-10 Ingersoll-Rand Industrial U.S., Inc. Multi-stage compressor having interstage lubricant injection via an injection rod
US11215182B2 (en) 2018-03-01 2022-01-04 Ingersoll-Rand Industrial U.S., Inc. Multi-stage compressor having interstage lubricant injection via an injection rod
US12146494B2 (en) 2018-03-01 2024-11-19 Ingersoll-Rand Industrial U.S., Inc. Multi-stage compressor having interstage lubricant injection via an injection rod
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Also Published As

Publication number Publication date
DE2240018A1 (de) 1973-06-14
DE2240018C3 (de) 1979-01-25
JPS4864509A (enrdf_load_stackoverflow) 1973-09-06
FR2164224A5 (enrdf_load_stackoverflow) 1973-07-27
GB1402435A (en) 1975-08-06
DE2240018B2 (de) 1978-05-11
CA962645A (en) 1975-02-11
JPS5653112B2 (enrdf_load_stackoverflow) 1981-12-16
ES409115A1 (es) 1976-03-01

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