EP1019633B1 - Schraubenverdichter - Google Patents

Schraubenverdichter Download PDF

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Publication number
EP1019633B1
EP1019633B1 EP98955416A EP98955416A EP1019633B1 EP 1019633 B1 EP1019633 B1 EP 1019633B1 EP 98955416 A EP98955416 A EP 98955416A EP 98955416 A EP98955416 A EP 98955416A EP 1019633 B1 EP1019633 B1 EP 1019633B1
Authority
EP
European Patent Office
Prior art keywords
screw
rotor
rotor assembly
axial
type
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP98955416A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1019633A1 (de
Inventor
Günter Kirsten
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.)
KT Kirsten Technologie-Entwicklung GmbH
Original Assignee
KT Kirsten Technologie-Entwicklung GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by KT Kirsten Technologie-Entwicklung GmbH filed Critical KT Kirsten Technologie-Entwicklung GmbH
Publication of EP1019633A1 publication Critical patent/EP1019633A1/de
Application granted granted Critical
Publication of EP1019633B1 publication Critical patent/EP1019633B1/de
Anticipated expiration legal-status Critical
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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of bearings
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof

Definitions

  • the invention relates to a screw compressor a housing in which a main rotor and a secondary rotor are arranged, each a shaft and have a screw rotor.
  • Screw compressors are used to make a gaseous Compress substance, such as air, and to be made available as compressed gas.
  • a screw compressor is known in which a main rotor driven by a motor, a secondary rotor drives.
  • the waves of the main and secondary rotor are at both ends by roller bearings stored radially. Furthermore, the waves are both Runner at one end by several ball bearings axially supported.
  • These thrust bearings carry the through the Gas compression occurring between the screw rotors Forces in the axial direction of the main and secondary rotor.
  • the roller bearings develop heat during operation an inhomogeneous heat distribution and thus tension lead in the wave.
  • the object of the invention is the storage of the main and Simplify the secondary rotor in a screw compressor and improve.
  • Secondary rotor axially supported on the main rotor.
  • the main rotor has a thrust bearing part that an axial bearing part of the housing is supported.
  • the secondary runner is only direct through radial bearings supported on the housing.
  • the runner is however no longer with its own axial bearing directly on the Supported housing.
  • the axial forces of the secondary rotor through its screw rotor onto the screw rotor of the main runner.
  • the thrust bearing of the Main rotor formed by the thrust bearing parts of the Main rotor and housing, so it takes all axial Forces of the main rotor and the secondary rotor.
  • the main rotor expediently has the only thrust bearing on, since larger axial on the main rotor Forces act as on the secondary runner. With this configuration only have the relatively low axial forces of the secondary rotor over the screw rotor teeth on the Main runners are transferred. Basically, however also the secondary rotor with an axial bearing be supported on the housing while the main rotor axially supported on the secondary rotor via the screw rotors and is not a separate thrust bearing with the housing having.
  • this is of the Thrust bearing parts formed thrust bearings a plain bearing.
  • the radial bearings can also be designed as plain bearings his.
  • the axial plain bearing is structurally simpler as a roller bearing and thereby facilitates a cheaper one Manufacture of the screw compressor.
  • Have plain bearings also the advantage of not generating any significant heat, so that the rotor shafts even at high speeds stay tension-free.
  • the plain bearing can with the be lubricated with the same medium as Lubricant and sealant in the compressor room of the Screw compressor is used.
  • Lubricating and sealing fluids can serve oil or water. However, air can also be used as the sliding bearing fluid become.
  • the Drive side preferably a roller bearing as a radial bearing used because the slide bearing is extremely flexible high radial loads are not suitable.
  • the secondary runner exclusively via the meshing teeth of the screw rotors axially supported on the main rotor.
  • the teeth the screw rotors can be designed such that there is very little or none at all on the secondary runner axial forces occur so that these small axial Forces of the secondary rotor can be easily applied via the screw rotor teeth can be transferred to the main runner.
  • the secondary rotor preferably has an axial clamping device that axially preloads the secondary runner.
  • the axial clamping device has no stop, to which the secondary runner could be supported, but acts on the secondary runner, preferably the Secondary rotor shaft, with a constant preload force, the approximate expected axial load of the secondary runner due to the gas compression.
  • the tensioning device compensates approximately the axial forces occurring on the secondary rotor, so that only very little or no axial forces from that Secondary runner must be transferred to the main runner.
  • the axial Clamping device a hydraulic clamping device, on the shaft or the screw rotor of the secondary rotor acts.
  • the clamping device can also be used Be fed by air.
  • the axial bearing part of the main rotor is preferably on the screw rotor of the main rotor. Not the shaft of the main rotor, but the screw rotor the main rotor is supported on the housing.
  • the thrust bearing part of the main rotor an axial end wall of the screw rotor.
  • the thrust bearing part of the housing is one washer-like tread, both axial bearing parts together form the plain bearing.
  • the front wall of the The main rotor screw rotor therefore forms a bearing surface, the on the ring-like tread of the housing outsourced.
  • the main runner on an axial end face of the screw rotor as Axial bearing part on a plain bearing disc, which with a Thrust bearing tread of the housing the plain bearing forms.
  • an annular slide bearing washer is provided, which forms a closed radial tread.
  • the screw rotor end wall or the plain bearing disc is essentially radial Grooves for a sliding fluid.
  • This Grooves can be the sliding fluid that is close to the shaft or on the base of the screw rotor is introduced by the centripetal forces continue to reach the outside. On this way, over the entire radius and perimeter of the screw rotor creates a sliding film.
  • the grooves an arcuate course, the radially outer End of each groove opposite to the direction of rotation of the rotor is bent. This results in very even results Sliding fluid distributions over the entire radius and Scope of the screw rotor.
  • the grooves preferably have a T-shaped course, the vertical part being radial and the horizontal part Part arranged tangentially in the circumferential direction are.
  • the T-shaped grooves allow a good one Plain bearing lubrication in both directions of the Main rotor.
  • the screw rotor, the shaft and the plain bearing washer of the main rotor integrally formed with each other.
  • the main runner can be cast from a composite material, Syringes etc. be made in a negative form.
  • the plain bearing disc can be formed separately and with the shaft and / or the screw rotor of the Main rotor cast, screwed or on others Be attached way.
  • the plain bearing disc and the main rotor can be different Materials for shaft, rotor and plain bearing disc can be chosen that correspond to the respective physical Requirements of the respective component better adapted can be.
  • the screw rotor can for example in a conventional manner, for example Composite, be milled and the metal plain bearing washer then screwed to the screw rotor become.
  • the shaft a special radial bearing running layer of the main and the secondary rotor applied.
  • the main runner can for example, be made in one piece, and on the Shaft then a super sliding material for the Radial bearings are applied.
  • the screw compressor 10 from a housing 12 in which axially parallel to each other a main rotor 14 and a secondary rotor 16 are arranged are.
  • the main rotor 14 consists essentially of a shaft 18, a screw rotor 20 and one Plain bearing washer 22, which acts as a thrust bearing part of the main rotor 14 serves.
  • the secondary runner 16 is in turn essentially from a shaft 24 and the Screw rotor 26. Both the shaft 24 and the Screw rotor 26 of the secondary rotor are in diameter each smaller than the shaft 18 and the screw rotor 20 of the main runner 14.
  • Both the main runner 14 and the secondary rotor 16 are also made in one piece from a composite material manufactured.
  • the main rotor 14 is a shaft extension 28, the is led out of the housing 12, driven. This drive is preferably carried out directly via a axially aligned with the main rotor longitudinal axis Electric motor.
  • the main rotor shaft 18 with two Radial bearings 30,32 stored in the housing 12. Also the Secondary rotor 16 is in the with two radial bearings 34,36 Housing 12 stored. All radial bearings are 30,32,34,36 designed as a plain bearing.
  • the one enclosed by the housing 12 Space in which the main rotor screw rotor 20 and the secondary rotor screw rotor 26 are arranged are, the compression space 27 of the screw compressor 10, in which the gas is compressed.
  • the housing 12 does not have one on the side of the shaft extension 28 shown gas opening into which to be compressed Gas can flow into the compression chamber 27.
  • the radial bearings 30, 32 and 36 are in principle all built up the same. Via a sliding fluid inlet 38, 39, 41 a sliding fluid, namely water, runs into an annular groove 44. Sits on the shaft 18, 24, each from the annular groove 44 surround a bearing bush 46, each three radial Has holes 48 through which the sliding fluid reach the outer circumference of the respective shaft 18, 24 can.
  • Secondary rotor 16 runs the sliding fluid through an axial Shaft bore 62 and three arranged at 120 ° to each other radial bores 64 of the shaft 24 to the shaft circumference or to the bearing bush 47. From there it runs Sliding fluid on the shaft circumference in the direction of the compression space 27th
  • the main rotor 14 has a thrust bearing 15, which as Plain bearing is formed.
  • the one axial bearing part of the Axial bearing 15 is formed by the plain bearing disc 22, which are arranged on the end face of the screw rotor 20 and axially closes it.
  • the other Axial bearing part is from an annular disk-like tread 66 of the housing 12 is formed.
  • the washer-like Running surfaces 66,68 of the plain bearing disc 22 and the housing 12 together form a plain bearing, which Screw rotor 20 of the main rotor 18 directly on the housing 12 supports.
  • the sliding fluid for the thrust bearing 15 is a Inlet 70 fed to an annular groove 72 of the main rotor shaft 18, which extends axially up to the slide bearing washer 22 extends.
  • the sliding fluid is at a pressure of approximately 10 bar supplied, which is approximately the gas pressure of the compressed gas corresponds.
  • the plain bearing disc 22 a plurality of radially and arched outwards, tapered grooves 23, due to the the centripetal forces occurring when the main rotor 14 rotates the sliding fluid comes out.
  • the sliding fluid emerges from the grooves 23 of the plain bearing disc 22 out and forms between the treads 66,68 of the thrust bearing 15, a fluid film for the sliding storage ensures.
  • the lubricating fluid continues to flow to the outside and finally gets into the compression space 27th
  • the secondary rotor 16 is with the teeth 25 of its screw rotor 26 with the teeth 21 of the screw rotor 20 of the main rotor 14 meshing. Over the tooth flanks the teeth 21 and 25 are axial forces of the Secondary rotor 16 on the teeth 21 of the main rotor 14 transfer.
  • a fluid space 76 is covered by a cover 78 of the Enclosed housing 12 in which the sliding fluid for Radial bearing 34 is introduced through the inlet 40.
  • the Lubricant works with its fluid pressure of approximately 10 bar on the end face 74 of the shaft 24 and generated therefore a force on the secondary rotor in the axial direction 16, which on the secondary runner 16 through the Counteracts gas pressure acting axial force.
  • This arrangement thus acts as a pneumatic clamping device, which axially cushions the secondary rotor 16, however no stop for fixing the secondary rotor 16 in a certain axial position.
  • Fig. 3 is a second embodiment of a plain bearing disc 22 'shown in the sliding fluid grooves 84 are arranged in a T-shape. It is the vertical groove 85 radial and the horizontal groove arranged tangentially. With this configuration the Grooves 84 can be the main rotor 14 'in both directions of rotation are operated, in both directions adequate lubrication is guaranteed.
  • a main rotor 90 is shown, the consists essentially of two parts: the shaft 92, which are made in one piece with the screw rotor 94 is, for example made of a composite material or Metal, and the slide bearing disc 22 ', which consists of a Material with good sliding properties is made.
  • the plain bearing disc 22 has four axial driver pins 95 on the corresponding holes in the Screw rotor 94 fit.
  • the plain bearing disc can be separated first manufactured and then when casting the main rotor 90 can be cast in.
  • FIG. 7 shows the main rotor 14 of FIG. 1.
  • a main rotor is shown in the the shaft 18 on both sides of the screw rotor 26 one radial bearing running layer 102 is applied in each case is, the better sliding properties than the shaft material has, and consist of so-called super sliding materials can.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Supercharger (AREA)
EP98955416A 1997-10-08 1998-10-08 Schraubenverdichter Expired - Lifetime EP1019633B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19744466A DE19744466C2 (de) 1997-10-08 1997-10-08 Schraubenverdichter
DE19744466 1997-10-08
PCT/EP1998/006389 WO1999018355A1 (de) 1997-10-08 1998-10-08 Schraubenverdichter

Publications (2)

Publication Number Publication Date
EP1019633A1 EP1019633A1 (de) 2000-07-19
EP1019633B1 true EP1019633B1 (de) 2003-01-15

Family

ID=7844952

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98955416A Expired - Lifetime EP1019633B1 (de) 1997-10-08 1998-10-08 Schraubenverdichter

Country Status (11)

Country Link
US (1) US6312239B1 (ja)
EP (1) EP1019633B1 (ja)
JP (1) JP2001519503A (ja)
KR (1) KR20010030985A (ja)
CN (1) CN1274410A (ja)
AT (1) ATE231220T1 (ja)
AU (1) AU743902B2 (ja)
DE (2) DE19744466C2 (ja)
ES (1) ES2191976T3 (ja)
RU (1) RU2212564C2 (ja)
WO (1) WO1999018355A1 (ja)

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6086345A (en) * 1999-02-05 2000-07-11 Eaton Corporation Two-piece balance plate for gerotor motor
BE1014043A3 (nl) * 2001-03-07 2003-03-04 Atlas Copco Airpower Nv Watergeinjecteerd schroefcompressorelement.
US7682084B2 (en) * 2003-07-18 2010-03-23 Kobe Steel, Ltd. Bearing and screw compressor
US7726115B2 (en) * 2006-02-02 2010-06-01 General Electric Company Axial flow positive displacement worm compressor
JP4387402B2 (ja) * 2006-12-22 2009-12-16 株式会社神戸製鋼所 軸受及び液冷式スクリュ圧縮機
BE1018158A5 (nl) * 2008-05-26 2010-06-01 Atlas Copco Airpower Nv Vloeistofgeinjecteerd schroefcompressorelement.
DE102010045881A1 (de) * 2010-09-17 2012-03-22 Pfeiffer Vacuum Gmbh Vakuumpumpe
DE102013020535A1 (de) * 2013-12-12 2015-06-18 Gea Refrigeration Germany Gmbh Verdichter
US10323636B2 (en) 2014-03-21 2019-06-18 Circor Pumps North America, Llc Gear pump with end plates or bearings having spiral grooves
CN104165139B (zh) * 2014-08-03 2016-04-20 浙江大学 啮合齿轮泵用滑动轴承自循环冷却油润滑系统
US20160208801A1 (en) * 2015-01-20 2016-07-21 Ingersoll-Rand Company High Pressure, Single Stage Rotor
CN107503840A (zh) * 2017-08-14 2017-12-22 于临涛 旋转发动机及气体压缩机改进
CN108757450B (zh) * 2018-05-14 2020-04-28 西安交通大学 一种采用滑动轴承的螺杆压缩机
JP7037448B2 (ja) * 2018-07-20 2022-03-16 株式会社日立産機システム スクリュー圧縮機本体
WO2020053976A1 (ja) 2018-09-11 2020-03-19 株式会社日立産機システム スクリュー圧縮機
CN109931261A (zh) * 2019-02-01 2019-06-25 宁波鲍斯能源装备股份有限公司 水润滑螺杆压缩机
CN112610607A (zh) * 2020-12-21 2021-04-06 英诺伟特（昆山）能源机械有限公司 一种无油水润滑轴承
CN113898582B (zh) * 2021-11-17 2023-12-22 宝风压缩机科技(宁波)有限公司 一种改进型螺杆空气压缩机
CN114985681B (zh) * 2022-06-21 2023-11-14 冰轮环境技术股份有限公司 一种螺旋转子铸造方法及加工装置

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FR789211A (fr) * 1935-04-24 1935-10-25 Cfcmug Moteur ou compresseur volumétrique rotatif
US2111883A (en) * 1936-04-17 1938-03-22 Burghauser Franz Pump
US2871794A (en) * 1953-06-01 1959-02-03 Roper Ind Inc Gear pump or fluid motor
SE317154B (ja) * 1959-01-15 1969-11-10 Svenska Rotor Maskiner Ab
US3275226A (en) * 1965-02-23 1966-09-27 Joseph E Whitfield Thrust balancing and entrapment control means for screw type compressors and similardevices
US3811805A (en) * 1972-05-16 1974-05-21 Dunham Bush Inc Hydrodynamic thrust bearing arrangement for rotary screw compressor
SE422348B (sv) * 1977-10-24 1982-03-01 Stal Refrigeration Ab Anordning vid en kompressor av rotationstyp for att fixera en rotoraxel i axiell led
DE3015551C2 (de) * 1980-04-23 1986-10-23 Mannesmann Rexroth GmbH, 8770 Lohr Kreiskolbenmaschine
US4730995A (en) * 1986-09-25 1988-03-15 American Standard Inc. Screw compressor bearing arrangement with positive stop to accommodate thrust reversal
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US5211026A (en) * 1991-08-19 1993-05-18 American Standard Inc. Combination lift piston/axial port unloader arrangement for a screw compresser
US5466137A (en) * 1994-09-15 1995-11-14 Eaton Corporation Roller gerotor device and pressure balancing arrangement therefor

Also Published As

Publication number Publication date
DE19744466A1 (de) 1999-04-22
ES2191976T3 (es) 2003-09-16
AU743902B2 (en) 2002-02-07
KR20010030985A (ko) 2001-04-16
AU1226599A (en) 1999-04-27
DE59806955D1 (de) 2003-02-20
US6312239B1 (en) 2001-11-06
DE19744466C2 (de) 1999-08-19
WO1999018355A1 (de) 1999-04-15
EP1019633A1 (de) 2000-07-19
JP2001519503A (ja) 2001-10-23
CN1274410A (zh) 2000-11-22
RU2212564C2 (ru) 2003-09-20
ATE231220T1 (de) 2003-02-15

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