US3467300A - Two-stage compressor - Google Patents

Two-stage compressor Download PDF

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Publication number
US3467300A
US3467300A US701323A US3467300DA US3467300A US 3467300 A US3467300 A US 3467300A US 701323 A US701323 A US 701323A US 3467300D A US3467300D A US 3467300DA US 3467300 A US3467300 A US 3467300A
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United States
Prior art keywords
rotor
working space
end plate
rotor elements
compressor
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US701323A
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English (en)
Inventor
Lauritz Benedictus Schibbye
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Svenska Rotor Maskiner AB
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Svenska Rotor Maskiner AB
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Publication date
Application filed by Svenska Rotor Maskiner AB filed Critical Svenska Rotor Maskiner AB
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Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F04C23/003—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle having complementary function
    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump

Definitions

  • the present invention relates to a two-stage compressor of the meshing screw rotor type.
  • a compressor comprises a housing composed of two barrel members separated by a partition, and two end plate members.
  • Each barrel member provides a working space composed of two intersecting, cylindrical bores with parallel axes and axially limited by high pressure ⁇ and low pressure end wall surfaces, provided by the partition and the adjacent end plate member.
  • At least one bore of one Working space is coaxial with a bore of the other working space and separated therefrom by the partition.
  • intermeshing male and female rotor elements are located for rotation around axes coinciding with those of the bores.
  • Each rotor element is provided with helical lands and grooves having an effective wrap angle of less than 360 degrees.
  • the lands and grooves of a male rotor element are located mainly outside the pitch circle of the rotor element and are provided with generally convex flanks, whereas the lands and grooves of a female rotor element are located mainly inside the pitch circle of the rotor element and are provided with generally concave flanks.
  • a male rotor element and a female rotor element cooperate with each other and with the wall surfaces of the working space to form chevron-shaped compression chambers, each com prising communicating groove portions of the cooperating rotor elements.
  • the base ends of the chevron-shaped chambers are located at the high pressure end wall surface of the working space, whereas the apices of the chevronshaped chambers move axially towards the base ends thereof, as the rotors revolve, whereby the volume of each chevron-shaped chamber decreases.
  • One rotor element in one working space is connected with an aligned rotor element in other working space to form a torsionally and axially rigid rotor unit extending through the partition and provided with radial bearings in the end plate members of the housing and with a thrust bearing in one of the end plate members only, whereas the other axial end of the axially rigid rotor unit must be axially free.
  • the lead angles of the lands and grooves of the two elements of the rotor unit are directed oppositely to each other, whereby the apices of the chevron-shaped compression chambers in the two sections move in opposite directions, so that the axial forces acting on the two rotor 3,467,300 Patented Sept. 16, 1969 elements of the rotor unit are counterdirected and partially balance each other.
  • One working space and the two cooperating rotor elements enclosed therein constitute a first compression stage.
  • This first stage is provided with an inlet port communicating with an inlet channel to the compressor which port has at least its major portion located at the low pressure end wall surface ofthe working space or within an larea adjacent thereto, and an outflow port communicating with an overflow channel between the two stages which outflow port has at least its major portion located at the high pressure end Wall surface of the working space or within an area adjacent thereto.
  • the second working space and the two cooperating rotor elements enclosed therein constitute a second compression stage.
  • This second stage is provided with an inow port communicating with the overow channel which inliow port has at least its major portion located at the low pressure end wall surface of the working space or within an area adjacent thereto and an outlet port communicating with an outlet channel from the compressor which outlet port has at least its major portion located at the high pressure end wall surface of the working space or within an area adjacent thereto.
  • the object of the present invention is to reduce the separation of the rotor elements without noticeable deterioration of the compressor in other respects.
  • the high pressure ports of the two stages i.e. the outflow port of the Iirst stage and the outlet port of the second stage, in accordance to the invention are located adjacent to the end plate members of the housing and the radial bearings for the rigid rotor unit have to be located in those members in the way already known per se. In this way the largest radial forces will act upon the rotor elements adjacent to the radial bearings thus reducing the deection of the rotor elements and consequently reducing the separation thereof.
  • the rotor unit is not only rotatably rigid in order to convey the required power to the different compression stages, but also axially rigid in order to provide the largest possible balancing of the axial forces deriving from the different stages, the rotor unit can be axially journalled only in one single thrust bearing.
  • the thrust bearing for the rigid rotor unit is in accordance to the invention located in the housing in the end plate member thereof facing the working space A of the second compression stage.
  • a compressor according to the invention is provided with means for injection of liquid into the working spaces of the dilerent stages, whereby the working fluid is effectively cooled and thus the heat transferred to the compressor structure is so limited that the temperature rise will fall within an acceptable range.
  • the female rotor element of the rst compression stage can not be connected with the male rotor unit by means of a synchronizing gear but has to be driven by direct flank contact between the flanks of the meshing lands and grooves of the cooperating rotor elements. Normally there will be such a iiank contact between the cooperating rotor elements also in the second compression stage.
  • FIG. l is a top view section of a two-stage compressor generally taken through the common plane of the rotor axes
  • FIG. 2 is a section taken along line II-II in FIG. 4,
  • FIG. 3 is a section taken along line III-lll in FIG 2, and
  • PIG. 4 is a section taken along line IV-IV in FIG. 2.
  • the compressor shown comprises a housing composed of a first barrel member 10, a second barrel member 12 integral with an end plate member 14, a partition 16 located between the barrel members 10, 12 and an end plate member 18 secured to the end of the barrel member remote from the partition 16.
  • Each of the two barrel members 10, 12 forms a working space 20 and 22, respectively, generally composed of two cylindrical, intersecting bores with parallel axes and axially closed by the partition 16 and the adjacent end plate member 14, 18. All four bores have the same diameter and each bore in one barrel member is in alignment with one bore in the other barrel member.
  • the working space 20 in the barrel member 10 is provided with an inlet port 24 having an axial section in the wall of the partition 16 and a radial section inthe portions of -the barrel wall adjacent thereto and communicating with an inlet channel 26 provided in the barrel member 10, in which inlet channel a splash plate 28 is located.
  • the working space 20 is further provided with an outliow port 30 having an axial section in the wall of the end plate member 1'8 and a radial section in the portions of the barrel wall adjacent thereto and communicating with an overflow channel 32 provided in the barrel mem- ,ber 10, the partition 16 and the barrel member 12.
  • working space 22 is correspondingly provided with an iniiow port 34 having an axial section in the wall of the partition 16 and a radial section in the portions of the barrel wall adjacent thereto and communicating with the overflow channel 32.
  • the working space 22 is further provided with an outlet port 36 having an axial section in the wall of the end plate member 14 and a radial section in the portions of the barrel wall adjacent thereto and communicating with an outlet channel 38 located in the barrel member 12.
  • a correspondingly shaped pair of intermeshing male and female rotor elements 44 and 46, respectively, are provided within the working space 22.
  • the male rotor element 40 is provided with a shaft 48 projecting therefrom and extending through the partition 16, the working space 22 and the end plate memfber 14 to form the driving shaft of the compressor.
  • the shaft is within the working space 22 provided with two annular interference surfaces 50, 52 separated by a shallow and relatively wide valley 54.
  • the male rotor element 44 is provided with a central bore having correspondingly formed interference surfaces and is shrunk on the shaft 48.
  • the rotor element 44 is further nonrotatably fixed to the shaft 48 by a pin 56.
  • the two male rotor elements 40, 44 form thus an axially and torsionally rigid rotor unit.
  • the interference surface 52 adjacent to the rotor element 40 has a slightly larger diameter than the surface 50 and the shaft is provided with a central channel 58 communicating with the valley 54 through a radial channel 60 for introduction of a high pressure liquid between the shaft 48 and the rotor element 44 in order to nullify the interference therebetween.
  • the rigid male rotor unit 40, 44 is mounted in bearings in the end plate members 14 and 18.
  • the bearing in the end plate member 18 is a radial bearing only and comprises a bushing 62 held in position vby a cover 64 vfixed to the end plate member 18 lby means of 'bolts not shown.
  • the bearing in the end plate member 14 is a combined radial and thrust bearing and comprises a bushing 66 having an end member 68 non-rotatably but slightly tiltably fixed thereto. The bushing is held in an axial position determined by the thickness of a washer 70 by means of a ring member 72.
  • the shaft 48 of the rotor unit 40, 44 is provided with a ring member 74 nonrotatably and axially fixed thereto which ring member 74 cooperates with the end member 68 to form a thrust bearing for axial forces trying to move the rotor unit 40, 44 towards the end plate member 18.
  • the bushing 66 is further provided with an end surface facing the rotor element 44 and cooperating therewith to form a thrust bearing for axial forces trying to move the rotor unit 40, 44 towards the end plate member 12.
  • the end plate member 14 is covered by a cap 76 and a sealing device 78 is provided at the opening through which the shaft 48 projects.
  • a bore in the partition is located in alignment with the shaft 48 projecting therethrough and provided with a sealing device 80 of labyrinth type cooperating with the shaft 48.
  • Shims are inserted between the 'barrel member 12 and the partition 16, between the partition 16 and the barrel member 10, and between the barrel member and the end plate member 18 in order to adjust the axial clearances between the rotor element 44 and the partition 16, between the partition 16 and the rotor element 40, and between the rotor element 40 and the end plate memiber 18, respectively.
  • the two female rotor elements 42, 46 are completely free from each other. Each of them is mounted correspondingly to the male rotor unit by means of a radial bearing in the partition 16 and in a combined radial and thrust bearing in the adjacent end plate member 18, 14.
  • the partition 16 is provided with an inlet channel 82 for supply of pressure oil from a source, not shown. From the channel 82 the oil is distributed to the working spaces 20, 22 through injection openings 84 and 86, respectively, to the sealing device 78 and to bearings for the female rotor element 42, 46 located in the partition 16. Pressure oil is further supplied to the space between the cover 64 and the confronting end of the male rotor unit 40, 44 for partial balancing of the axial forces acting on the unit. Oil is also supplied to the bearings not specifically mentioned above.
  • the oil injected into the working spaces 20, 22 serves except for as a lubricant between the cooperating flanks of the rotor elements 40, 42, 44, 46 and as a sealing agent for the clearances between the intermeshing rotor elements and between the rotor elements and the walls of the working spaces also as a cooling agent for the working Ifluid during the compression thereof resulting in a much lower temperature of the working fluid and thus in a small transfer of -heat to the structure of the compressor which means so low a temperature of the housing and the rotor elements that the thermal expansion thereof results in negligible deformations only.
  • the compressor shown acts in the following way.
  • Working fluid is supplied to the inlet channel 26 and passes through the inlet port 24 to the working space 20, where it enters the grooves of the rotor elements 40 ⁇ and 42.
  • the fluid is then during the rotation of the rotor elements 40, 42 transferred to the compression phase of the first stage and compressed therein and delivered therefrom through the outflow port 30 to the overflow channel 32.
  • oil is injected into the working space 20 through the injection opening 84 for cooling, sealing and lubricating purposes.
  • the Working fluid are directed and distributed in such a way that the axial forces acting upon the elements 40, -44 of the male rotor unit counteract each other, which together with the axial force acting on the rotor unit by the pressure oil enclosed by the cover 64 reduces the load on the thrust bearing 68, 74 to a minimum, and that the radial forces acting upon the rotor elements 40, 42, 44, 46 have their maximum values close to the end plate members 14, 18 where the radial Ibearings are 1ocated which means that the deflections of the rotor elements 40, 42, 44, 46 are reduced to a minimum.
  • the small deflections of the rotor elements and the negligible thermal deformations thereof and of the housing means that the clearances in the compressor necessary with respect to the mechanical reliability can be kept smaller than those otherwise necessary which means that the internal leakage will be further reduced resulting in a still higher efficiency of the compressor.
  • Two-stage compressor of the meshing screw rotor type comprising a housing composed of two barrel members, a partition and two end plate members, providing a working space in each of said barrel members, each working space being generally composed of intersecting cylindrical bores with parallel axes and axially limited 'by the partition and the adjacent end plate member, at least one bore of one working space being in coaxial alignment with a bore of the other working space, intermeshing male and female rotor elements being mounted in the housing for rotation in each of said working spaces, each rotor element being provided with helical lands and intervening grooves having an effective wrap angle of less than 360, one rotor element in one working space being connected with a coaxially aligned rotor element in the other working space to form a torsionally and axially rigid rotor unit, the lands and grooves of each male rotor element being located mainly outside the pitch circle of the element and provided with generally convex flanks, the lands and grooves of each female rotor element being located mainly inside the

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US701323A 1967-02-06 1968-01-29 Two-stage compressor Expired - Lifetime US3467300A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB5592/67A GB1220054A (en) 1967-02-06 1967-02-06 Two-stage compressor of the meshing screw rotor type

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US3467300A true US3467300A (en) 1969-09-16

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BE (1) BE710157A (en)van)
CH (1) CH478990A (en)van)
CS (1) CS152450B2 (en)van)
FI (1) FI47598C (en)van)
FR (1) FR1555022A (en)van)
GB (1) GB1220054A (en)van)
SE (1) SE318053B (en)van)

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3733152A (en) * 1971-10-29 1973-05-15 Warren Pumps Inc Rotary pump
WO1988007137A1 (en) * 1987-03-19 1988-09-22 Svenska Rotor Maskiner Ab Screw rotor machine
US4792294A (en) * 1986-04-11 1988-12-20 Mowli John C Two-stage screw auger pumping apparatus
US4944657A (en) * 1989-03-01 1990-07-31 Mowli John C Two-stage pumping apparatus with low shear first stage
US5139399A (en) * 1991-10-18 1992-08-18 Ingersoll-Rand Company Compressor interstage coolant injector nozzle
US5267837A (en) * 1992-09-23 1993-12-07 Mowli John C Two-stage pumping apparatus with non-meshing first stage augers
US5951266A (en) * 1992-09-03 1999-09-14 Matsushita Electric Industrial Co., Ltd. Evacuating apparatus having interengaging rotors with threads having a decreasing pitch at the exhaust side
US6257195B1 (en) 2000-02-14 2001-07-10 Arthur Vanmoor Internal combustion engine with substantially continuous fuel feed and power output
US20060165335A1 (en) * 2003-07-18 2006-07-27 Kabushiki Kaisha Kobe Seiko Sho(Kobe Steel, Ltd.) Bearing and screw compressor
US20110158841A1 (en) * 2009-12-28 2011-06-30 Sunny King Machinery Co., Ltd. Screw Pump with Anti-Turbulent Structure
US20130146035A1 (en) * 2011-12-09 2013-06-13 Eaton Corporation Air supply system with two-stage roots blower
CN104005950A (zh) * 2013-02-26 2014-08-27 复盛股份有限公司 流体机械的多段式螺旋转子机构
US9039396B2 (en) 2012-07-03 2015-05-26 Emerson Climate Technologies, Inc. Piston and scroll compressor assembly
CN104948451A (zh) * 2015-05-29 2015-09-30 浙江威隆机械科技有限公司 一种衬套螺杆泵
US9360011B2 (en) 2013-02-26 2016-06-07 Emerson Climate Technologies, Inc. System including high-side and low-side compressors
CN110206729A (zh) * 2019-05-27 2019-09-06 西安交通大学 一种具有气体止推轴承的自平衡轴向力四螺杆机械装置
CN110397589A (zh) * 2019-08-26 2019-11-01 珠海格力电器股份有限公司 具有平衡轴向力功能的双级螺杆压缩机及空调机组
CN112780557A (zh) * 2021-02-26 2021-05-11 珠海格力电器股份有限公司 一种转子结构、压缩机和空调
CN112797001A (zh) * 2021-02-26 2021-05-14 珠海格力电器股份有限公司 转子组件、压缩机及空调
CN113383163A (zh) * 2019-02-06 2021-09-10 株式会社日立产机系统 多级螺杆压缩机
US11149732B2 (en) 2017-11-02 2021-10-19 Carrier Corporation Opposed screw compressor having non-interference system
US11286933B2 (en) * 2017-06-05 2022-03-29 Gree Electric Appliances (Wuhan) Co., Ltd Multi-stage compressor and air conditioner
CN114320910A (zh) * 2020-12-02 2022-04-12 珠海格力电器股份有限公司 螺杆压缩机和空调系统
CN115479027A (zh) * 2022-10-25 2022-12-16 珠海格力电器股份有限公司 双级螺杆压缩机及空调机组
WO2023093179A1 (zh) * 2021-11-26 2023-06-01 珠海格力电器股份有限公司 压缩机以及空调
US11725658B2 (en) 2016-08-02 2023-08-15 Johnson Controls Air Conditioning And Refrigeration (Wuxi) Co., Ltd. Screw compressor with male and female rotors
US20240141896A1 (en) * 2021-03-23 2024-05-02 Hitachi Industrial Equipment Systems Co., Ltd. Multi-stage screw compressor

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EP2473739B1 (de) * 2009-08-31 2014-03-26 Ralf Steffens Trockene schraubenpumpe mit innerer verdichtung
CN113417851B (zh) * 2021-08-12 2025-01-10 珠海格力节能环保制冷技术研究中心有限公司 螺杆压缩机和空调器
CN116146487A (zh) * 2022-12-08 2023-05-23 珠海格力电器股份有限公司 双螺杆压缩机及制冷设备

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US3184155A (en) * 1963-04-17 1965-05-18 Cooper Bessemer Corp Motor compressor unit
US3265292A (en) * 1965-01-13 1966-08-09 Svenska Rotor Maskiner Ab Screw rotor machine
US3279682A (en) * 1963-02-23 1966-10-18 Howden James & Co Ltd Screw air compressors
US3307777A (en) * 1963-12-23 1967-03-07 Svenska Rotor Maskiner Ab Screw rotor machine with an elastic working fluid

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3279682A (en) * 1963-02-23 1966-10-18 Howden James & Co Ltd Screw air compressors
US3184155A (en) * 1963-04-17 1965-05-18 Cooper Bessemer Corp Motor compressor unit
US3307777A (en) * 1963-12-23 1967-03-07 Svenska Rotor Maskiner Ab Screw rotor machine with an elastic working fluid
US3265292A (en) * 1965-01-13 1966-08-09 Svenska Rotor Maskiner Ab Screw rotor machine

Cited By (41)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3733152A (en) * 1971-10-29 1973-05-15 Warren Pumps Inc Rotary pump
US4792294A (en) * 1986-04-11 1988-12-20 Mowli John C Two-stage screw auger pumping apparatus
WO1988007137A1 (en) * 1987-03-19 1988-09-22 Svenska Rotor Maskiner Ab Screw rotor machine
US4944657A (en) * 1989-03-01 1990-07-31 Mowli John C Two-stage pumping apparatus with low shear first stage
US5139399A (en) * 1991-10-18 1992-08-18 Ingersoll-Rand Company Compressor interstage coolant injector nozzle
US5951266A (en) * 1992-09-03 1999-09-14 Matsushita Electric Industrial Co., Ltd. Evacuating apparatus having interengaging rotors with threads having a decreasing pitch at the exhaust side
US5267837A (en) * 1992-09-23 1993-12-07 Mowli John C Two-stage pumping apparatus with non-meshing first stage augers
US6530365B2 (en) 1999-05-18 2003-03-11 Arthur Vanmoor Fluid displacement pump with backpressure stop
US6257195B1 (en) 2000-02-14 2001-07-10 Arthur Vanmoor Internal combustion engine with substantially continuous fuel feed and power output
US20060165335A1 (en) * 2003-07-18 2006-07-27 Kabushiki Kaisha Kobe Seiko Sho(Kobe Steel, Ltd.) Bearing and screw compressor
US7682084B2 (en) * 2003-07-18 2010-03-23 Kobe Steel, Ltd. Bearing and screw compressor
US20110158841A1 (en) * 2009-12-28 2011-06-30 Sunny King Machinery Co., Ltd. Screw Pump with Anti-Turbulent Structure
US9074524B2 (en) * 2011-12-09 2015-07-07 Eaton Corporation Air supply system with two-stage roots blower
US20130146035A1 (en) * 2011-12-09 2013-06-13 Eaton Corporation Air supply system with two-stage roots blower
US9039396B2 (en) 2012-07-03 2015-05-26 Emerson Climate Technologies, Inc. Piston and scroll compressor assembly
US10378539B2 (en) 2013-02-26 2019-08-13 Emerson Climate Technologies, Inc. System including high-side and low-side compressors
CN104005950A (zh) * 2013-02-26 2014-08-27 复盛股份有限公司 流体机械的多段式螺旋转子机构
CN104005950B (zh) * 2013-02-26 2016-04-13 复盛股份有限公司 流体机械的多段式螺旋转子机构
US9360011B2 (en) 2013-02-26 2016-06-07 Emerson Climate Technologies, Inc. System including high-side and low-side compressors
US9611849B2 (en) 2013-02-26 2017-04-04 Emerson Climate Technologies, Inc. System including high-side and low-side compressors
CN104948451A (zh) * 2015-05-29 2015-09-30 浙江威隆机械科技有限公司 一种衬套螺杆泵
US11725658B2 (en) 2016-08-02 2023-08-15 Johnson Controls Air Conditioning And Refrigeration (Wuxi) Co., Ltd. Screw compressor with male and female rotors
US11286933B2 (en) * 2017-06-05 2022-03-29 Gree Electric Appliances (Wuhan) Co., Ltd Multi-stage compressor and air conditioner
US11149732B2 (en) 2017-11-02 2021-10-19 Carrier Corporation Opposed screw compressor having non-interference system
EP3922853A4 (en) * 2019-02-06 2022-11-09 Hitachi Industrial Equipment Systems Co., Ltd. MULTI-STAGE SCREW COMPRESSOR
US11773853B2 (en) 2019-02-06 2023-10-03 Hitachi Industrial Equipment Systems Co., Ltd. Multi-stage screw compressor
CN113383163A (zh) * 2019-02-06 2021-09-10 株式会社日立产机系统 多级螺杆压缩机
CN113383163B (zh) * 2019-02-06 2023-05-16 株式会社日立产机系统 多级螺杆压缩机
CN110206729A (zh) * 2019-05-27 2019-09-06 西安交通大学 一种具有气体止推轴承的自平衡轴向力四螺杆机械装置
CN110206729B (zh) * 2019-05-27 2020-05-19 西安交通大学 一种具有气体止推轴承的自平衡轴向力四螺杆机械装置
CN110397589A (zh) * 2019-08-26 2019-11-01 珠海格力电器股份有限公司 具有平衡轴向力功能的双级螺杆压缩机及空调机组
CN110397589B (zh) * 2019-08-26 2023-10-10 珠海格力电器股份有限公司 具有平衡轴向力功能的双级螺杆压缩机及空调机组
CN114320910A (zh) * 2020-12-02 2022-04-12 珠海格力电器股份有限公司 螺杆压缩机和空调系统
WO2022179130A1 (zh) * 2021-02-26 2022-09-01 珠海格力电器股份有限公司 转子组件、压缩机及空调
CN112797001A (zh) * 2021-02-26 2021-05-14 珠海格力电器股份有限公司 转子组件、压缩机及空调
CN112780557A (zh) * 2021-02-26 2021-05-11 珠海格力电器股份有限公司 一种转子结构、压缩机和空调
CN112797001B (zh) * 2021-02-26 2024-11-15 珠海格力电器股份有限公司 转子组件、压缩机及空调
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WO2023093179A1 (zh) * 2021-11-26 2023-06-01 珠海格力电器股份有限公司 压缩机以及空调
CN115479027A (zh) * 2022-10-25 2022-12-16 珠海格力电器股份有限公司 双级螺杆压缩机及空调机组

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GB1220054A (en) 1971-01-20
SE318053B (en)van) 1969-12-01
FR1555022A (en)van) 1969-01-24
FI47598C (fi) 1974-01-10
CH478990A (de) 1969-09-30
CS152450B2 (en)van) 1973-12-19
FI47598B (en)van) 1973-10-01
BE710157A (en)van) 1968-05-30

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