EP0828940B1 - Compresseur a vis - Google Patents

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Publication number
EP0828940B1
EP0828940B1 EP96916081A EP96916081A EP0828940B1 EP 0828940 B1 EP0828940 B1 EP 0828940B1 EP 96916081 A EP96916081 A EP 96916081A EP 96916081 A EP96916081 A EP 96916081A EP 0828940 B1 EP0828940 B1 EP 0828940B1
Authority
EP
European Patent Office
Prior art keywords
rotors
rotor
primary
screw
compressor
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
EP96916081A
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German (de)
English (en)
Other versions
EP0828940A1 (fr
Inventor
Günter Kirsten
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Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0828940A1 publication Critical patent/EP0828940A1/fr
Application granted granted Critical
Publication of EP0828940B1 publication Critical patent/EP0828940B1/fr
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
    • 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
    • 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
    • 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
    • F04C2240/51—Bearings for cantilever assemblies

Definitions

  • the invention relates to a screw compressor a main rotor shaft, on which at least a first and a second main rotor rotor are arranged, the with a matching first and second secondary rotor comb on a spider shaft.
  • screw compressors To a gaseous substance, for example air compress it and make it available as compressed gas, screw compressors are used. These screw compressors must adhere to the operating conditions of the compressing gas must be matched, it being in particular it depends on the gas in a desired Quantity and with the desired pressure available too put. In addition, there are often purity requirements for the gas placed so that an oil lubrication under Circumstances is not permitted.
  • the amount of compressed gas and that with the screw compressor achievable gas pressure depends on the rotor geometry of the the rotors used in the screw compressor and the rotational speed of the rotors. However, it has shown that because of the occurring on the rotor circumference Peripheral speeds and due to sealing problems between the rotors of a screw compressor stage the increase in rotational speed and the rotor diameter are limited.
  • Such a double screw compressor is from DE 30 31 801 A1 known.
  • This screw compressor has one left and a right-angled main rotor on the face to face in a connection level then arranged on a common shaft are and also arranged on a common shaft corresponding corresponding ends left and right-angled secondary rotor comb.
  • This screw compressor it will gaseous medium to be compressed to the center of the compressor transported from where it is discharged in the radial direction becomes.
  • the "enclosed bag” designated effect and a good pressure gas transport to ensure the two pairs of rotors relative to each other on Wilnkel offset, so that the forming enclosed pocket of one Pair of rotors each in the still open gear of the trailing opposite rotor pair vented can be. Since the rotor pairs meet in the middle, are the main and the secondary rotor shaft on their opposite outer ends stored.
  • GB 650 606 is a screw compressor with one pair of rotors each having known main and secondary rotor shaft, the stored at their ends and in the middle between the rotors are. There is a large number of bearings for the rotor shafts used by bearings, which means a great deal of construction work and manufacture of the screw compressor is required.
  • the invention has for its object a screw compressor to make available yourself with little effort can be made.
  • the two secondary rotor and the second main rotor on one side.
  • Such a cantilever Storage has the advantage of changing the ratio D / L (diameter / rotor length) is easily possible and that the construction of new screw compressors with changed L / D ratio and thus changed swallowing volume the design new rotor geometries are not required because the cantilevered rotors can be easily shortened.
  • the wear of the screw compressor is reduced that the bearing of the main and secondary rotor shaft on the Compressed gas routing is matched by that occurring Pressures caused loads on the shafts close to their location Radial acting bearings are included.
  • This type of storage allows tighter tolerances to be selected, so that a higher efficiency can be achieved.
  • the invention also has the advantage that the effort for the storage is reduced, causing the screw compressor is cheaper to produce.
  • the number of rotors per shaft is not limited. Basically three and also more rotors can be provided. If however, two rotors are provided, these two are preferred spaced axially from each other. The axial distance between the rotors it allows both the main rotor shaft as well also the secondary rotor shaft in the area between the main rotor rotors or to store the secondary rotor, so that at one Derivation of the compressed gas in the area between the rotors emerging forces can also be absorbed in this area.
  • the The rotor geometries of the main rotor rotors are coordinated with one another in such a way that that the compressed gas forces acting in the axial direction of the two main rotor rotors at least partially, and preferably fully compensate. Compensation in the axial direction acting gas pressure forces, which arise from the axial direction effective areas and the area on the area in question Pressure results in wear and tear the bearing effort for the main rotor shaft can be reduced.
  • an adjusting device provided in the secondary rotor shaft for setting an axial distance between the two secondary rotor it is possible to run the secondary rotor independently from each other and from the main rotor rotors, wherein the game between the main rotor rotors and each Secondary rotor afterwards with the adjusting device can be adjusted.
  • This configuration not only reduces the Manufacturing effort, but minimized also those that occur during operation of the screw compressor Blowback losses, since narrow tolerances are used can.
  • a partition is arranged between two each of a main rotor with compressor stages formed by a secondary rotor. With this partition you can the uncontrolled overflow of compressed gases from a compressor stage be prevented in the other compressor stage. Preventing overflow is particularly advantageous if if the screw compressor is in a kind of tandem operation to be operated, the pressure medium to be compressed first the first and then the second compressor stage flows through. With this configuration, it is advantageous to cool in the first compressor stage by water injection. In the second compressor stage there is water injection then not necessary. When the screw compressor is used with successively flowing compressor stages it is advantageous for the first and second compressor stage different To provide rotor geometries that correspond to the respective volume change are adjusted.
  • the rotors can be 5: 7 or 6: 7 toothed. Larger number of teeth lead to poor swallowing volume, with small ones The number of teeth makes the tooth height too high and the corresponding rotor shaft too thin.
  • the preferred 5: 7 toothing of the rotors leads to a weak pulsating compressed gas flow with low noise and good strength properties.
  • the screw compressor 10 has a housing 12, inside which there are two ceramic main rotor rotors 14.16 main rotor shaft and a two ceramic Secondary rotor rotors 20, 22 carrying secondary rotor shaft 24 are arranged are.
  • Inside the housing 12 of the screw compressor 10 forms the first main rotor rotor 14 with the first secondary rotor rotor 22 a first compressor stage 26 leading to a from the second main rotor 16 to the second sub rotor 20 formed second compressor stage 28 with respect to the Compressed gas flow is arranged in parallel.
  • the operation of the screw compressor 10 is by the Arrangement of the two compressor stages 26, 28 in the housing 12 and by the type of storage of the main rotor shaft 18 and Secondary shaft 24 influenced, it should be emphasized that the housing 12 accommodating all the rotors 14, 16, 20, 22 in several parts is constructed.
  • the housing 12 has a central, along the plane of the rotor axes divided bearing block 30 with flanged to it laterally Jacket parts 32.34.
  • So-called Cover flaps formed on the suction side the rotors 14, 16, 20, 22 are arranged and for this purpose serve, thrown away from the rotors 14,16,20,22 Coolants and lubricants.
  • bearing block 30 To support the main and secondary rotor shaft 18,24 are in the bearing block 30 two split bearings per shaft 40,42,44,46 provided, the lower bearing shells 48a to 48d in a bearing block lower part 50 and the upper one Bearing shells 52a to 52d in a bearing block upper part 54 of the bearing block 30 are arranged.
  • the bearing shells 48a to 48d, 52a to 52d, those not shown Lubricant holes for oil or water lubrication are provided, and directly adjacent to the rotors are arranged, encompass the respective shaft absorb radial forces.
  • the screw compressor 10 is connected to the Main rotor shaft 18 integrally formed drive shaft 56 driven, which on one of the end faces of the Screw compressor 10 through the second end cover 38 protrudes through and opposite the end cover 38 is mounted by means of a needle bearing 58.
  • a needle bearing 58 To the second closed by the second end cover 38 Sealing compressor stage 28 to the outside is one that Drive shaft 56 sealing against the housing 12 Sealing arrangement 60 is provided.
  • the screw compressor 10 is driven by Rotate the drive shaft 56 counterclockwise the arrow A. This rotation turns the first and the second cast on the main rotor shaft 18 Main rotor rotor 14.16 driven. Indirectly via the main rotor rotors driven by the main rotor shaft 18 14, 16 are the meshing with these secondary rotor 20.22 driven.
  • the leadership of the gas to be compressed can be on easiest seen from Figure 3.
  • the thing to be compressed Gas is initially on the top 62 of the upper part of the bearing block 54 fed to the screw compressor 10. This can either directly or indirectly via suction filter and intake cooler. From the top 62 of the bearing block upper part 54 located inlet opening 64, the gas is first to the two ends of the Screw compressor 10 passed. From the front the screw compressor 10 distributes the compressed gas above which the first and second compressor stages 26, 28 main and secondary rotor rotors 14, 16, 20, 22.
  • the Main rotor rotors 14, 16 each have five teeth comb with seven teeth of the secondary rotor 20.22. To avoid axial forces acting on the outside one of the two main rotor rotors 14 is slanted to the right, whereas the other main rotor 16 is slanted to the left is.
  • the two main rotor rotors are 14, 16 on the main rotor shaft 18 without mutual angular misalignment arranged. Because the two main rotor rotors 14, 16 also have a corresponding length, they stand on the teeth of the main rotor rotors 14,16 acting pressure gas forces, so that the Bearing of the main rotor shaft 18 an axial guide not required.
  • the screw compressor 10 is manufactured by that first on a pre-machined main rotor shaft 18 cast the two main rotor rotors 14, 16 become. In the same way, the secondary rotor 20.22 around a pre-machined secondary rotor shaft 24 poured around. Both waves 18,24 are then into their respective lower cups 48a inserted up to 48d. Then the bearing block 30 closed by the finished top block 54 with the upper bearing shells arranged therein 52a to 52d placed on the bearing block lower part 50 becomes. The centering is done like this already at the finishing of the upper block 54 and the bearing block lower part by centering sleeves, the for centering the upper part of the bearing block 54 and the lower part of the bearing block 50 clamping fittings 76 arranged surrounding are.
  • the split design of the bearing block 30 This greatly facilitates implementation the finishing and finishing of the individual components and the assembly of the screw compressor 10.
  • the second embodiment of a shown in FIG Screw compressor 110 differs from that first embodiment of a screw compressor 10 only in a few details. Parts, parts at the correspond to the first embodiment, are therefore with provided with a reference symbol which is opposite the corresponding Reference numerals in FIGS. 1 to 4 around 100 is increased. Regarding the description of these parts will refer to the description of the first embodiment referred.
  • the main rotor rotors 114, 116 and the secondary rotor rotors 120, 122 are in the second embodiment as in the first embodiment with a main rotor shaft 118 or a secondary rotor shaft 124 rotatably connected.
  • the secondary shaft 124 faces in contrast to the first embodiment, an adjusting device 180 for setting the axial distance of the secondary rotor rotors 120, 122 from each other.
  • the adjuster 180 is within the idler shaft 124 designed so that a conical projection 182 of a first secondary rotor partial shaft 184 in a conical recess 186 of a second secondary rotor partial shaft 188 protrudes.
  • the two are independent of each other Secondary rotor partial shafts 184, 188 are by means of one in the axial direction of the two secondary rotor part shafts extending clamping screw 190 connected and together form the secondary rotor shaft 124.
  • an adjusting device can also be provided at of the two secondary rotor partial waves with each other superimpose cylindrical sections.
  • the distance of the Auxiliary rotors can then be tightened using a clamping screw and inserted disc springs.
  • the second embodiment of screw compressor 110 further additional Shaft bearings 192a to 192c on the the End covers 136, 138 facing end faces the secondary rotor 120, 122 and on one of the end covers 136 facing end of the Main rotor rotor 114 are arranged.
  • the shaft bearings 192a to 192c each have one in the respective end cover 136, 138 fixed circular cylindrical bearing journals 194a to 194c, the bearing bush 196a rotating with the respective rotor intervenes until 196c.
  • the bearing bushes 196a to 196 are in turn in bearing openings 198a to 198c, the cylindrical recesses are arranged, having an interference fit and at the front end of the respective main or secondary rotor Complete 114, 120, 122 with the respective end face.
  • the arrangement of the bearing bushes 196a to 196c in The rotors 114, 120, 122 become the overall length of the screw compressor shortened.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Supercharger (AREA)

Claims (10)

  1. Compresseur à vis comportant un arbre d'induit principal (18 ; 118) sur lequel sont agencés au moins un premier et un deuxième rotor d'induit principal (14, 16 ; 114, 116) qui s'engrènent avec respectivement un premier et un deuxième rotor d'induit auxiliaire adapté (20, 22 ; 120, 122) agencés sur un arbre d'induit auxiliaire (24 ; 124),
       les rotors d'induit principal (14, 16 ; 114, 116) et les rotors d'induit auxiliaire (20, 22 ; 120, 122) étant à chaque fois à une certaine distance axiale l'un de l'autre et l'arbre d'induit principal (18; 118) et l'arbre d'induit auxiliaire (24 ; 124) étant montés dans la zone située entre les rotors d'induit principal (14, 16 ; 114, 116) ou les rotors d'induit auxiliaire (20, 22 ; 120, 122),
       caractérisé en ce que l'arbre d'induit auxiliaire (24) et l'arbre d'induit principal (18) sont montés de telle sorte que les deux rotors d'induit auxiliaire (20, 22) et l'un des rotors d'induit principal (14) sont agencés de manière à dépasser librement d'un côté.
  2. Compresseur à vis selon la revendication 1, caractérisé en ce que le fluide comprimé est évacué selon la direction axiale des rotors d'induit principal et d'induit auxiliaire (14, 16, 20, 22 ; 114, 116, 120, 122).
  3. Compresseur à vis selon la revendication 1 ou 2, caractérisé en ce que les géométries de rotor des rotors d'induit principal (14, 16 ; 114, 116) sont adaptées l'une à l'autre de telle sorte que les forces de gaz comprimé, agissant en direction axiale, des deux rotors d'induit principal (14, 16 ; 114, 116) se compensent au moins en partie.
  4. Compresseur à vis selon l'une des revendications 1 à 3, caractérisé en ce que les géométries de rotor des rotors d'induit principal (14, 16 ; 114, 116) sont adaptées l'une à l'autre de telle sorte que les forces de gaz comprimé, agissant en direction axiale, des deux rotors d'induit principal (14, 16 ; 114, 116) se compensent totalement.
  5. Compresseur à vis selon l'une des revendications 1 à 4, caractérisé en ce que les géométries de rotor des rotors d'induit auxiliaire (20, 22 ; 120, 122) sont adaptées l'une à l'autre de telle sorte que les forces de gaz comprimé, agissant en direction axiale, des deux rotors d'induit auxiliaire (20, 22 ; 120, 122) se compensent au moins en partie.
  6. Compresseur à vis selon l'une des revendications 1 à 5, caractérisé en ce que le premier rotor d'induit principal (14 ; 114) et le deuxième rotor d'induit principal (16 ; 116) ont des géométries symétriques par rapport à un plan.
  7. Compresseur à vis selon la revendication 6, caractérisé en ce que le premier et le deuxième rotor d'induit principal (14, 16 ; 114, 116) sont agencés sur l'arbre d'induit principal (18 ; 118) sans décalage angulaire mutuel de telle sorte que l'évolution temporelle de la pression au premier rotor d'induit principal (14 ; 114) coïncide avec celle au deuxième rotor d'induit principal (16 ; 116).
  8. Compresseur à vis selon l'une des revendications 1 à 7, caractérisé en ce que l'arbre d'induit principal et/ou l'arbre d'induit auxiliaire (124) comportent un dispositif de réglage (180) pour régler la distance axiale des deux rotors d'induit principal ou des deux rotors d'induit auxiliaire (120, 122) l'un par rapport à l'autre.
  9. Compresseur à vis selon l'une des revendications 1 à 8, caractérisé en ce que le premier rotor d'induit principal (14 ; 114) forme avec le premier rotor d'induit auxiliaire (20 ; 120) un premier étage de compresseur (26 ; 126), en ce que le deuxième rotor d'induit principal (16 ; 116) forme avec le deuxième rotor d'induit auxiliaire (22 ; 122) un deuxième étage de compresseur (28 ; 128) et en ce qu'une paroi de séparation est agencée entre les deux étages de compresseur (26, 28 ; 126, 128) agencés dans un carter commun (112).
  10. Compresseur à vis selon l'une des revendications 1 à 9, caractérisé en ce que les rotors (14, 16, 20, 22 ; 114, 116, 120, 122) comportent une denture 5:7.
EP96916081A 1995-05-25 1996-05-15 Compresseur a vis Expired - Lifetime EP0828940B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19519247A DE19519247C2 (de) 1995-05-25 1995-05-25 Schraubenverdichter
DE19519247 1995-05-25
PCT/EP1996/002078 WO1996037706A1 (fr) 1995-05-25 1996-05-15 Compresseur a vis

Publications (2)

Publication Number Publication Date
EP0828940A1 EP0828940A1 (fr) 1998-03-18
EP0828940B1 true EP0828940B1 (fr) 2001-08-16

Family

ID=7762866

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96916081A Expired - Lifetime EP0828940B1 (fr) 1995-05-25 1996-05-15 Compresseur a vis

Country Status (6)

Country Link
US (1) US6093008A (fr)
EP (1) EP0828940B1 (fr)
JP (1) JPH11505911A (fr)
AT (1) ATE204362T1 (fr)
DE (2) DE19519247C2 (fr)
WO (1) WO1996037706A1 (fr)

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DE19945871A1 (de) * 1999-09-24 2001-03-29 Leybold Vakuum Gmbh Schraubenpumpe, insbesondere Schraubenvakuumpumpe, mit zwei Pumpstufen
US6478560B1 (en) * 2000-07-14 2002-11-12 Ingersoll-Rand Company Parallel module rotary screw compressor and method
JP2003343469A (ja) * 2002-03-20 2003-12-03 Toyota Industries Corp 真空ポンプ
JP2004346864A (ja) * 2003-05-23 2004-12-09 Taiko Kikai Industries Co Ltd 廃熱回収用膨張機関
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JP5663798B2 (ja) * 2013-05-30 2015-02-04 オリオン機械株式会社 二軸回転ポンプ
JP5663794B2 (ja) * 2013-05-30 2015-02-04 オリオン機械株式会社 二軸回転ポンプ
WO2014192851A1 (fr) * 2013-05-30 2014-12-04 オリオン機械株式会社 Pompe rotative à deux arbres
JP5663796B2 (ja) * 2013-05-30 2015-02-04 オリオン機械株式会社 二軸回転ポンプ
JP5663795B2 (ja) * 2013-05-30 2015-02-04 オリオン機械株式会社 二軸回転ポンプ
US10006340B2 (en) * 2013-10-16 2018-06-26 John Malcolm Gray Supercharger
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
DE102015113698B4 (de) * 2015-08-19 2021-11-11 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Kompressoreinheit mit angeflanschtem Elektromotor
CN110177918B (zh) 2017-01-11 2022-04-01 开利公司 具有螺旋叶转子的流体机械
US11149732B2 (en) * 2017-11-02 2021-10-19 Carrier Corporation Opposed screw compressor having non-interference system
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
CN114320910B (zh) * 2020-12-02 2023-05-19 珠海格力电器股份有限公司 螺杆压缩机和空调系统

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Also Published As

Publication number Publication date
JPH11505911A (ja) 1999-05-25
EP0828940A1 (fr) 1998-03-18
US6093008A (en) 2000-07-25
WO1996037706A1 (fr) 1996-11-28
DE59607504D1 (de) 2001-09-20
DE19519247C2 (de) 2000-08-31
DE19519247A1 (de) 1996-11-28
ATE204362T1 (de) 2001-09-15

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