EP1163452A1 - Schraubenkompressor - Google Patents
SchraubenkompressorInfo
- Publication number
- EP1163452A1 EP1163452A1 EP00922512A EP00922512A EP1163452A1 EP 1163452 A1 EP1163452 A1 EP 1163452A1 EP 00922512 A EP00922512 A EP 00922512A EP 00922512 A EP00922512 A EP 00922512A EP 1163452 A1 EP1163452 A1 EP 1163452A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- housing
- rotor
- rotor housing
- gear
- rotors
- 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.)
- Granted
Links
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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/025—Lubrication; Lubricant separation using a lubricant 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
- 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
-
- 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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
- F04C27/009—Shaft sealings specially adapted for pumps
-
- 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
- F04C2240/00—Components
- F04C2240/60—Shafts
- F04C2240/605—Shaft sleeves or details thereof
Definitions
- the invention relates to a screw compressor of the type mentioned in the preamble of claim 1.
- the invention is preferably, but not exclusively, applicable to a screw compressor for generating a compressed air flow for the pneumatic transport of bulk materials, and in particular for a device designed for attachment to a silo vehicle Screw processor.
- Screw compressors are air compressors working according to the displacement principle, which have advantageous properties compared to other compressor types, which make them particularly suitable for the pneumatic transport of bulk materials.
- the contact-free running of the rotors means that there is no wear in this area, which reduces the service life, and there is no abrasion that can contaminate the required air.
- Screw compressors are suitable because of their operating characteristics, especially for the realization of high-pressure conditions and are resistant to short-term increases in pressure caused by obstruction of the could with the compressed air ⁇ acted pipeline caused. After all, they are lighter in weight and less measurements, which are particularly useful for mobile applications. B. makes suitable for silo vehicles.
- the compressor housing is designed as an oil pan below the two rotors. This has u. a. the disadvantage that there is a strong thermal coupling between the compressor chamber and the oil reservoir, so that the 01 in the reservoir is heated to a considerable extent by the heat generated in the compressor chamber due to the compressor operation.
- the invention is based, to achieve the greatest possible thermal separation of the oil reservoir from the actual compressor room, the construction of the compressor house.
- Figure 1 is a perspective view of the compressor with suction filter, seen from the side.
- Fig. 2 is a vertical section through the compressor of Fig. 1;
- FIG. 4 shows a further perspective view of the compressor from below, seen from the suction end, with the suction housing and oil container removed;
- FIG. 5 shows a detail of the perspective view according to FIG. 1, with a modified embodiment of the intake housing
- Fig. 6 is an enlarged detail of the sectional view of Fig. 2 in the area of the suction-side rotor bearing.
- FIG. 7 shows an enlarged detail of the sectional illustration of FIG. 3 in the area of the rotor bearing on the pressure side.
- a gear housing 1 a gear housing 1
- a rotor housing 3 an inflow housing 4
- an intake housing 5 an oil container 7.
- the rotor housing 3 there are two rotors, namely a major rotor 9 (profiled tooth) and a secondary rotor 11 (profile hatches) are rotatably mounted, which mesh with one another with their helical teeth and tooth spaces and thereby form sealed chambers which move and shrink in the axial direction when the rotor rotates and thereby compress the sucked-in air.
- the rotors are driven so that their right end in FIGS. 1-3 is the suction side.
- air is drawn in through inflow openings 13 provided on the end face of the rotor housing 3.
- the air is required to the left by the interlocking teeth and tooth spaces of the rotor pair in the axial direction and exits as compressed air at the pressure-side end of the rotors at an upward pressure outlet 15.
- the principle of operation of a screw compressor is known and is not explained in more detail here.
- the gear housing 1 has the shape of a disk-like stand. Bearings 16, 18 support the drive shaft 17 of the compressor, the shaft journal 17a of which protrudes from the housing cover 49 is connected to a rotary drive (not shown).
- the gear housing 1 also contains a drive gear, consisting of a gear 19 fastened on the drive shaft 17 and a gear 21 fastened on the shaft journal 23 of the secondary rotor 11, through which the rotation of the drive shaft 17 is transmitted to the secondary rotor 11 with a suitable transmission ratio.
- the synchronizing gear which ensures the synchronous operation of these rotors is accommodated, consisting of the intermeshing gear wheels 25, 27 which are on the shaft journal 23 of the secondary rotor or on the shaft journal 29 of the Main rotor 9 are attached.
- the synchronizing gear ensures that the roto- ren 9, 11 with very little play, but mesh without contact. This makes it possible to manage without any oil lubrication between the rotors 9, 11, ie to implement a dry-running compressor. This is particularly important if the compressor is to generate an air flow absolutely free of oil pressure levels for the pneumatic feeding of sensitive material.
- the overall stand or disk-shaped gear housing 1 has on its lower base surface on both sides projecting mounting feet 31 with holes 33 for mounting screws with which the entire compressor on a suitable base, for. B. a vehicle can be attached.
- lubricating oil is injected into the area of the toothing engagement of both gears, which is continuously circulated by an oil pump 45.
- An orderly supply of 01 is kept in stock in the oil container 7, which communicates with the interior of the get ⁇ e housing 1.
- Sealing arrangements 35 interact with the shaft journals 23, 29 of the rotors 9, 11 and prevent oil from entering the rotors 9, 11 and thus to the compression chamber of the compressor. These sealing arrangements will be explained in more detail.
- the rotor housing 3 is fastened to the gear housing 1 by means of a flange connection 37 in such a way that it projects freely from the gear housing 1.
- the oil container 7, which has a flat box shape, is attached to the gear housing 1 in such a way that it projects freely therefrom, approximately parallel to the rotor housing 3 and below it.
- the side walls of the oil container 7 are provided with cooling fins 39.
- An oil pump 45 which surrounds and is driven by the drive shaft 17, serves for the circulation of the oil in the interior of the transmission housing 1, or for generating an oil mist.
- the housing of the oil pump 45 has an outwardly projecting flange 47, which serves to center the housing cover 49 fastened to the transmission housing 1.
- the oil pump 45 is fastened to the transmission housing 1 with 4 screws 51 (FIG. 3) and associated threaded holes.
- the ends of the suction-side shaft journals 55, 57 of the rotors 9, 11 projecting beyond the bearings 53 are provided with a tool engagement for the attachment of a turning tool.
- the tool engagement consists of two flats 63 for the attachment of a spanner.
- the tool engagement can also have the shape of a square, hexagon, hexagon socket or the like.
- the shaft journals 55, 57 provided with the tool engagement are easily accessible by removing a housing cover 65 fastened with screws on the inflow housing 4.
- the suction housing 5 contains a filter 6 made of a suitable porous or air-permeable filter material.
- the filter lies in an air flow path between an outer suction slot 69 and a passage slot 73 arranged in an inner partition 71, suction slot 69 and passage slot being offset from one another such that the longest possible flow path for the air between the slots 69, 73 through the filter 6 is formed.
- suction housing 5 shows a modified embodiment of the suction housing 5, in which the air sucked in through the suction slot 69 and deflected by the deflecting wall 71 with a passage slot 73 flows through a muffler 75 formed, for example, from suitable perforated metal sheets, before it enters the housing cover 69 enters the surrounding space and flows through the emstrom openings 13 into the interior of the rotor housing 3. It is also possible to design the suction housing 5 such that it contains both a filter and a muffler.
- the advantage of directly attaching the suction housing 5 containing a filter and / or a muffler to the rotor housing 3 in such a way that it surrounds the inflow housing 4 at a distance is that a separate arrangement of a filter and / or muffler and a connection line between this and the suction side of the compressor can be omitted. A particularly simple, compact and robust arrangement is thereby achieved.
- a further advantage is that the air sucked into the suction housing 5 flows around and cools the outside of the inflow housing 4 containing the shaft journal bearings before it enters the interior of the rotor housing 3 through the flow openings 13. As a result, effective cooling of the suction-side rotor bearings is achieved.
- FIG. 6 shows an enlarged sectional view of the mounting and sealing of the shaft journal 55 of the rotor 9 m in the Emstromgehause 4.
- the shaft journal 57 of the other rotor 11 is mounted and sealed in an analogous manner.
- the shaft pin 57 provided with the tool engagement (flats 63) is mounted in the middle part of the Emstrom housing 4, which is designed in the manner of a hub, by means of a roller bearing 53 which is arranged between a shoulder of the shaft pin 57 and a locking ring 83 engaging in an annular groove of the shaft pin.
- the roller bearing 53 is preferably designed as an encapsulated bearing with a lifetime grease filling so that it does not require any additional lubrication.
- a race 85 is fastened on the shaft journal 57, preferably shrunk on.
- the race 85 which is, for example, a commercial sub- can be a race for e roller bearings, is made of steel with a specially hardened peripheral surface. Two sealing lips of a lip seal 87, which seals the interior of the rotor housing 3 against the roller bearings 53, cooperate with this.
- a protective ring 89 is arranged between the latter and an inner shoulder 4a of the emstrom housing 4, the inner circumference of which lies opposite the outer surface of the race 85 with a very small gap, but without contact.
- the protective ring 89 and the lip seal 87 are fixed to one another and adjoining the inner shoulder 4a of the Emstromgepuruses 4 in the bore of the housing, preferably glued.
- the function of the protective ring 89 is as follows: In operation, the compressor generates a compressed air flow by sucking in air on the suction side and blowing out compressed air at the pressure port 15, which e.g. can be used for the pneumatic transport of dusty goods. In the event of operational malfunctions, compressed air may kick back from the pressure side to the suction side of the rotors, which means that there is a risk that particles of the dust-like material carried by air flow will get into the rotor housing 3 and out of this to the shaft journals of the rotors. In the case of such a material pressure blow, the protective ring 89 protects the lip seal 87 from dust particles getting under the sealing lips of the lip seal 87 and impairing the sealing effect.
- the suction-side bearing arrangement shown in FIG. 6 and described above has the further advantage that it can be pulled off the shaft journal 57 without the rotor 9 or 11 being removed or the precise E- Position of the rotors to each other must be changed.
- the bearing and sealing arrangement can be removed from the shaft journal in the following way:
- the housing cover 65 of the inflow housing 4 is removed, so that the shaft journal 57 with its locking ring 83 is accessible.
- the snap ring 83 is removed.
- the screws connecting the inflow housing 4 to the rotor housing 3 are loosened.
- the entire inflow housing 4 together with the roller bearings 53, lip sealing rings 87 and protective rings 89 contained therein can be removed.
- the suction-side roller bearings 53 which are the parts that are most likely to be replaced due to the limited service life of their grease filling, can be easily replaced without the rotors 9, 11 having to be adjusted or even removed in relation to one another and to the housing.
- FIG. 7 shows in a sectional view corresponding to FIG. 3, but on a larger scale, the mounting and sealing of the pressure-side shaft journals 29, 23 of the rotors 9, 11 at the pressure-side end of the rotor housing 3.
- the bearing and sealing arrangement for the shaft journal 29 will be described below of the rotor 9 described.
- the one for the shaft journal 23 of the rotor 11 is completely analog.
- the shaft journal 29 is supported in the pressure-side end wall of the rotor housing 3 by two roller bearings 91, 93 arranged next to one another, which are designed as so-called angular contact ball bearings.
- Angular contact ball bearings which are commercially available, are ball bearings whose balls from the outer and inner race only on one side or the other radial central plane are encompassed.
- the two angular contact ball bearings 91, 93 are arranged side by side in mirror symmetry. Such an arrangement of angular contact ball bearings has the property that it is completely free of play in the axial direction.
- a shaft nut 95 arranged on the shaft journal 29 fixes the angular contact ball bearings 91, 93 m in the axial direction on the shaft journal 29.
- the outer running of the angular contact ball bearing 93 bears against an inner shoulder 97 of the rotor housing 3.
- This barrel 101 is fastened, preferably shrunk on.
- This barrel 101 like the barrel 85 described above in accordance with FIG. 6, consists of steel with a specially hardened peripheral surface.
- the sealing lips of a lip seal 103 which seals the compression space of the rotor housing 3 against the oil-loaded transmission and bearing area, rest on the surface of the race 101.
- the hardened and extremely precisely machined, e.g. The polished outer surface of the race 25 results in a particularly wear-reducing contact surface for the sealing lips of the lip seal 103.
- labyr thdichtrmg 105 which has several adjacent ring ribs on its inner circumference, which face the outer surface of the race 101 with a very small gap but without contact and form a labyrinth gap with it.
- the barrel 101 does not normally have any contact with the labyrinth seal 105, it is nevertheless advantageous that the bore 101 also covers the area of the labyrinth seal 105 extends.
- the labyrinth gap seal is normally a non-contact seal, but it can happen under extreme operating conditions that there may be contact between the ring ribs of the labyrinth seal ring 105 and the running ring 101.
- the mouth of the lantern 109 lies at a distance from the with the cooling ribs 39 provided top of the oil container 7 opposite. A straight access path to the mouth of the lantern 109 from below is blocked by the oil container 7.
- FIG. 4 shows a perspective view from below of the compressor with the oil container 7 removed, so that the screw holes 44 for fastening the oil container 7 and the large connection opening 43, via which the oil container communicates with the transmission housing, m the front wall of the transmission housing 1. are visible.
- the suction housing 5 is removed from the suction-side end of the rotor housing 3, so that there is a clear view of the house 4 with its support ribs 14 and the emstrom openings 13 leading to the interior of the rotor housing 3.
- FIG. 4 also shows the mouth of the lantern (ventilation duct) 109 on the underside of the rotor housing 3.
- the mouth of the lantern 109 is provided with projections 111 on the underside of the rotor housing 3, which shield the mouth of the lantern 109 against straight access from the side.
- These projections 111 can be formed by oil drainage channels.
- the mouth of the lantern 109 is thus in a protected location to which a straight access path is not possible either from below (because of the oil container 7) or from the side (because of the protrusions 111). This prevents that, for example, when cleaning the compressor by means of a high-pressure sprayer, the high-pressure water jet can be directed directly onto the mouth of the lantern 109, as a result of which water could get into the annular space 107 and thus into the area of the lip seal 103 and the labyrinth seal ring 105.
- the rotor 101 mounted on the shaft journal 29 additionally serves as a spacing element, which is used to maintain a very precisely dimensioned gap between the pressure-side end face of the rotor 9 or 11 and the end face 113 of the rotor housing 3 facing it serves.
- a gap that is as small and precisely defined as possible on the pressure-side end face of the rotor 9 or 11.
- this gap is set and maintained precisely in such a way that, when machining the rotor assembly 3, the distance a between the end face 113 facing the rotor 9 and the contact shoulder 97 for the rolling bearing 93 is manufactured with very tight tolerances to a predetermined value.
- the length b of the race 101 which is used as a spacing element between the roller bearing 97 and the end face of the rotor 9, is also ground with correspondingly precise tolerances to a value which has an oversize compared to the distance a, which is exactly the width of the between the Corresponds to rotor 9 and the rotor housing 3 gap to be set.
- This adjustment of the gap due to the length difference of the distances a and b is possible in that angular contact ball bearings 91, 93 m of symmetrical arrangement are used according to the invention, which, as mentioned, result in a bearing arrangement that is completely free of axial play.
- the distance a between the housing shoulders and the length b of the race 101 can be obtained with sufficient accuracy a correspondingly precise setting of the rotor front gap.
- the setting of the rotor end gap once obtained is retained even when the temperature changes, since the influence of the different thermal expansion of rotor housing 3 and rotor 101 is negligibly small. There is no longer any need to adjust the rotor front gap when installing compressors of this type by inserting shims of different thicknesses in accordance with the fluctuations in the manufacturing tolerance.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Supercharger (AREA)
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE29904409U DE29904409U1 (de) | 1999-03-10 | 1999-03-10 | Schraubenkompressor |
DE29904409U | 1999-03-10 | ||
PCT/EP2000/002151 WO2000053932A1 (de) | 1999-03-10 | 2000-03-10 | Schraubenkompressor |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1163452A1 true EP1163452A1 (de) | 2001-12-19 |
EP1163452B1 EP1163452B1 (de) | 2004-05-19 |
Family
ID=8070664
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00922512A Expired - Lifetime EP1163452B1 (de) | 1999-03-10 | 2000-03-10 | Schraubenkompressor |
Country Status (5)
Country | Link |
---|---|
US (1) | US6416302B1 (de) |
EP (1) | EP1163452B1 (de) |
AT (1) | ATE267344T1 (de) |
DE (2) | DE29904409U1 (de) |
WO (1) | WO2000053932A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7713039B2 (en) | 2005-12-08 | 2010-05-11 | Gmbh Rand Schraubenkowpressoren Gmbh | Helical screw compressor having a vented sealing arrangement |
Families Citing this family (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100996016B1 (ko) * | 2000-09-20 | 2010-11-22 | 밀리포어 코포레이션 | 폴리뉴클레오티드 |
JP3796210B2 (ja) * | 2002-11-01 | 2006-07-12 | 株式会社神戸製鋼所 | スクリュ圧縮機 |
US6858067B2 (en) * | 2002-11-12 | 2005-02-22 | Perry Equipment Corporation | Filtration vessel and method for rotary gas compressor system |
JP4673136B2 (ja) * | 2005-06-09 | 2011-04-20 | 株式会社日立産機システム | スクリュー圧縮機 |
US8342829B2 (en) * | 2005-12-08 | 2013-01-01 | Ghh Rand Schraubenkompressoren Gmbh | Three-stage screw compressor |
JP2008121479A (ja) * | 2006-11-10 | 2008-05-29 | Hitachi Appliances Inc | 密閉形スクリュー圧縮機 |
US20090129956A1 (en) * | 2007-11-21 | 2009-05-21 | Jean-Louis Picouet | Compressor System and Method of Lubricating the Compressor System |
JP2009162129A (ja) * | 2008-01-08 | 2009-07-23 | Kobe Steel Ltd | スクリュ圧縮機 |
US8162625B1 (en) * | 2009-09-22 | 2012-04-24 | Harry Soderstrom | Nested motor, reduction motor reduction gear and pump with selectable mounting options |
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 |
EP2635814B8 (de) * | 2010-09-23 | 2020-06-17 | Ingersoll-Rand Company | Modularer druckschalldämpfer für einen fahrzeugmontierten kompressor |
CN106640639B (zh) * | 2015-10-29 | 2018-07-06 | 复盛股份有限公司 | 变段式压缩机 |
US10451061B2 (en) | 2016-05-06 | 2019-10-22 | Ingersoll-Rand Company | Compressor having non-contact and contact seals |
AU2017261926B2 (en) | 2016-05-12 | 2021-04-08 | Golden Renewable Energy, LLC | Cyclonic condensing and cooling system |
US10436525B2 (en) | 2016-05-12 | 2019-10-08 | Golden Renewable Energy, LLC | Cyclonic cooling system |
US20170361268A1 (en) * | 2016-06-21 | 2017-12-21 | Golden Renewable Energy | Char separator |
US10961062B2 (en) | 2016-06-21 | 2021-03-30 | Golden Renewable Energy, LLC | Bag press feeder assembly |
CR20190020A (es) | 2016-06-21 | 2019-04-25 | Golden Renewable Energy Llc | Separador de carbón y método |
WO2018007964A1 (en) | 2016-07-05 | 2018-01-11 | Golden Renewable Energy, LLC | System and process for converting waste plastic into fuel |
US10233393B2 (en) | 2016-07-08 | 2019-03-19 | Golden Renewable Energy, LLC | Heated airlock feeder unit |
EP3382203B1 (de) | 2017-03-30 | 2024-05-15 | Roper Pump Company LLC | Exzenterschneckenpumpe mit integriertem heizmantel |
CN109915365B (zh) * | 2019-04-04 | 2023-11-17 | 烟台东德氢能技术有限公司 | 罗茨式空气压缩机 |
WO2023237955A1 (en) * | 2022-06-09 | 2023-12-14 | Atlas Copco Airpower, Naamloze Vennootschap | Housing for housing a gearbox of a rotary screw compressor. |
BE1030612B1 (nl) * | 2022-06-09 | 2024-01-15 | Atlas Copco Airpower Nv | Behuizing voor het onderbrengen van een tandwielkast van een schroefcompressor |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3016184A (en) * | 1959-01-19 | 1962-01-09 | Scaife Company | Rotary compressors |
US3407996A (en) | 1966-06-22 | 1968-10-29 | Atlas Copco Ab | Screw compressor units |
FR1528285A (fr) * | 1966-06-22 | 1968-06-07 | Atlas Copco Ab | Groupe de compression à compresseurs à rotors hélicoïdaux |
JPS6293491A (ja) * | 1985-10-21 | 1987-04-28 | Hitachi Ltd | スクリユ−圧縮機 |
JP2511870B2 (ja) * | 1986-03-20 | 1996-07-03 | 株式会社日立製作所 | スクリユ−真空ポンプ装置 |
JPH08189483A (ja) * | 1995-01-06 | 1996-07-23 | Tochigi Fuji Ind Co Ltd | コンプレッサ |
US5772418A (en) * | 1995-04-07 | 1998-06-30 | Tochigi Fuji Sangyo Kabushiki Kaisha | Screw type compressor rotor, rotor casting core and method of manufacturing the rotor |
US5795136A (en) * | 1995-12-04 | 1998-08-18 | Sundstrand Corporation | Encapsulated rotary screw air compressor |
DE29807796U1 (de) * | 1998-04-30 | 1999-09-09 | Ghh Rand Schraubenkompressoren | Dichtungsanordnung für einen Wellenzapfen eines trockenlaufenden Rotationsschraubenverdichters |
-
1999
- 1999-03-10 DE DE29904409U patent/DE29904409U1/de not_active Expired - Lifetime
-
2000
- 2000-03-10 WO PCT/EP2000/002151 patent/WO2000053932A1/de active IP Right Grant
- 2000-03-10 AT AT00922512T patent/ATE267344T1/de not_active IP Right Cessation
- 2000-03-10 DE DE50006496T patent/DE50006496D1/de not_active Expired - Lifetime
- 2000-03-10 EP EP00922512A patent/EP1163452B1/de not_active Expired - Lifetime
-
2001
- 2001-09-10 US US09/950,322 patent/US6416302B1/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO0053932A1 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7713039B2 (en) | 2005-12-08 | 2010-05-11 | Gmbh Rand Schraubenkowpressoren Gmbh | Helical screw compressor having a vented sealing arrangement |
Also Published As
Publication number | Publication date |
---|---|
DE29904409U1 (de) | 2000-07-20 |
US20020048523A1 (en) | 2002-04-25 |
ATE267344T1 (de) | 2004-06-15 |
US6416302B1 (en) | 2002-07-09 |
WO2000053932A1 (de) | 2000-09-14 |
DE50006496D1 (de) | 2004-06-24 |
EP1163452B1 (de) | 2004-05-19 |
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