EP1242742A1 - Pompe a vide a vis refroidie - Google Patents

Pompe a vide a vis refroidie

Info

Publication number
EP1242742A1
EP1242742A1 EP00983238A EP00983238A EP1242742A1 EP 1242742 A1 EP1242742 A1 EP 1242742A1 EP 00983238 A EP00983238 A EP 00983238A EP 00983238 A EP00983238 A EP 00983238A EP 1242742 A1 EP1242742 A1 EP 1242742A1
Authority
EP
European Patent Office
Prior art keywords
rotor
coolant
pump according
cavity
shaft
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
Application number
EP00983238A
Other languages
German (de)
English (en)
Other versions
EP1242742B1 (fr
Inventor
Hartmut Kriehn
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.)
Leybold GmbH
Original Assignee
Leybold Vakuum GmbH
Leybold Vacuum 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 Leybold Vakuum GmbH, Leybold Vacuum GmbH filed Critical Leybold Vakuum GmbH
Publication of EP1242742A1 publication Critical patent/EP1242742A1/fr
Application granted granted Critical
Publication of EP1242742B1 publication Critical patent/EP1242742B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F04C29/04—Heating; Cooling; Heat insulation
    • 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

Definitions

  • the invention relates to a screw vacuum pump with two shafts and one rotor each carried by the shafts, each having a cavity; in each of the cavities there is another cavity which is part of a coolant circuit; the shafts have bores open towards the pressure side, through which the coolant is supplied and removed to and from the other cavities.
  • a screw vacuum pump with these features is known from DE-A-198 20 523 ( Figure 4).
  • the coolant is injected into the bores in the shafts, which are open on the pressure side.
  • the shafts are equipped with radial bores through which the coolant enters the rotor cavities.
  • the outer walls of these cavities are designed to widen conically in the direction of the pressure side.
  • the hot coolant returns to the respective central shaft bore via radial bores arranged in the shaft on the pressure side and flows back through these bores to their respective mouths.
  • a disadvantage of the previously known solution is that the cold coolant flows in and the hot coolant flows out through a common bore in the shafts.
  • the coolant first reaches the cooler side of the rotors (suction side) and then flows to the pressure side, where the compression heat to be dissipated is highest the technology a conical design of the respective rotor cavities ahead, which can only be manufactured with relatively great effort.
  • the object of the present invention is to improve not only the coolant supply to the rotor cavities but also the effectiveness of the cooling in a screw vacuum pump of the type mentioned at the outset.
  • the central shaft bore for housing the guide component can be a relatively large one Diameter. Compared to individual, separate deep-hole bores for supply and discharge channels of the coolant in the shaft material itself, it is much easier to manufacture. Furthermore, the guide components allow the rotors to be cooled in the “countercurrent”, since even a trouble-free crossing of the coolant flows to be carried in and out can be made possible.
  • FIGS. 1 to 7. Show it
  • FIG. 1 shows a section through a screw vacuum pump according to the invention
  • FIGS. 2 and 3 sections through one of two overhung rotors of a screw vacuum pump, which show further solutions for the design of the guide component
  • FIG. 4 shows a section through a rotor with means for displacing the cooling gap to the outside
  • FIG. 7 shows a solution with a rotor consisting of two sections.
  • the screw vacuum pump 1 shown in FIG. 1 comprises the pump chamber housing 2 with the rotors 3 and 4. Inlet 5 and outlet 6 of the pump 1 are schematically indicated by arrows.
  • the rotors 3 and 4 are fastened on the shafts 7 and 8, which are each supported in two bearings 11, 12 and 13, 14, respectively.
  • a pair of bearings 11, 13 is located in a bearing disc 15, which separates the lubricant-free scooping space from a gear space 16.
  • the second pair of bearings 12, 14 is located in the pump chamber housing 2.
  • In the housing 17 of the gear chamber 16 are the synchronization gears 18, 19 mounted on the shafts 7 and 8 and a gear pair 21, 22 serving to drive the pump 1, one of which with the Shaft of the drive motor 23 arranged vertically next to the pump 1 is coupled.
  • the transmission space has the function of an oil sump 20.
  • the oil sump 16 is separated from the oil-containing space 26 by seals 28, 29.
  • the second pair of bearings 12, 14 is located in the area of the bores 24, 25.
  • FIG. 1 shows that the rotors 3 and 4 each have a cavity 31 into which the shaft 8 extends and in which there is a further space 32 through which a coolant flows. Since only the rotor 4 is shown in partial section, the invention is only explained with reference to this rotor 4.
  • the space 32 through which the coolant flows is designed as an annular gap section and is located directly between shaft 8 (or 7) and rotor 4 (or 3).
  • the cylindrical inner wall of the rotor cavity 31 is provided in its central region with a recess 33, the depth of which corresponds to the thickness of the cooling gap 32.
  • the shaft 8 of the inner wall of the cavity lies on the suction side and the pressure side
  • the cooling gap 32 is supplied with the coolant via the shaft 8. It is equipped with a central bore 41 which extends from the lower end of the shaft 8 to the pressure-side end of the cooling gap 32. It forms a space 43 in which there is a guide component 44 for the coolant.
  • the guide component 44 extends from the lower end of the shaft 8 to the pressure-side end of the cooling gap
  • the coolant is supplied via the longitudinal bore 45 in the guide component 44, which is connected to the pressure-side end of the cooling gap 32 via cross-bores 46 aligned with one another through the component 44 and the shaft 8.
  • the shaft 8 is equipped with one or more transverse bores 47 which open into the space 43 formed by the blind bore 41 and the end face of the guide component 44.
  • the latter is connected to the transmission space 16 via the longitudinal bore 48 and the mutually aligned transverse bores 49 (in the guide component 44 and in the shaft 8).
  • the coolant is supplied from the oil-containing space 26 via the bores 45 and 46 into the cooling gap 32. It flows through the cooling gap 32 from the pressure side to the suction side of the rotor 4. Since the heat to be dissipated is largely generated on the pressure side of the rotor 4 the rotor 4 is cooled in counterflow.
  • the coolant is first discharged through the second bore 47 into the space 43 in the shaft 8 and through the bores 48, 49.
  • the bore 48 extends from the suction side of the cooling gap 32 to the height of the gear chamber 16.
  • the transverse bore 48 provides the connection of the bore 43 with the gear chamber 16 ago.
  • the gear chamber 16 or the oil sump 20 is connected to the chamber 26 via a line 51 in which, in addition to a cooler 52 and a filter 53, there is an oil pump 54 which is designed, for example, as a gear pump.
  • the oil pump 54 ensures that the coolant with the necessary pressure enters the bore 41 from the space 26 without cavitation.
  • oil pumps centrifugal pumps, gear pumps
  • these must be designed in such a way that they meet the requirements for the desired conveying properties.
  • FIG. 2 shows a solution in which the guide component 44 comprises three sections 61, 62, 63, which subdivide the cavity in the shaft 8 into three partial spaces 64, 65, 43, which are each located at the level of the transverse bores 49, 46 and 47 ,
  • a suitable supply and discharge of the coolant to the cooling gap can be realized by suitable bores in sections 61 to 63 and line sections 67 and 68, which connect these bores to one another.
  • the coolant is supplied through the bore 45, which, in contrast to the embodiments according to FIGS. 1 and 2, passes through the guide component 44 centrally.
  • the oil pumped into the bore 45 by a centrifugal pump 71 reaches into the cavity 43 formed by the blind bore 41 and the guide component 44 and via the transverse bore 46 into the space 32 through which the coolant flows.
  • the space 32 through which the coolant flows is one relatively large-volume annular space, which is formed by the shaft 8 and the inner wall of the rotor cavity 31.
  • the coolant injected from the bores 46 into the space 32 is conveyed in the direction of the rotor pressure side. It is not necessary to operate the coolant circuit without bubbles or cavitation.
  • the coolant can be metered in such a way that it flows along the inner wall of the rotor cavity 31, for example in the form of a thin film.
  • exit bores 47 are connected to lateral longitudinal grooves 72 (or a free rotation) in the guide component 44, which extend at the level of the bearing disc 15 to the gear chamber 16 and are there connected to the transverse bores 49.
  • the embodiment according to FIG. 4 differs from the embodiments described above in that the shaft 8 and the rotor 4 are drilled through continuously.
  • a cover 76 is provided on the suction side, which is connected to the guide component 44 via a screw 77.
  • the guide component 44 is firmly inserted from the suction side. It serves together with the screw 77 and the Cover 76 of the axial fixation of the rotor 4.
  • the bore 41 On the pressure side, the bore 41 has a smaller diameter.
  • the shaft 8 is equipped with an outer sleeve 77 which, together with the inner wall of the cavity 31 in the rotor 4, forms the cooling gap 32. This extends essentially only at the level of the pressure side of the rotor 4. The radial displacement of the cooling gap 32 to the outside improves the cooling effect.
  • the coolant is supplied only via relatively short longitudinal groove sections 78 (or a free rotation, annular channel) in the guide component 44 up to the transverse bores 46 which penetrate the shaft 8 and the sleeve 77. Before it enters the longitudinal grooves 78, it flows through bores 79, 80 in the bearing disk 15 and the bearing-side space 82 of a mechanical seal 83 and provides the necessary blocking pressure there. The coolant is returned via the transverse bores 47 and the central bore 45 in the guide component 44 or the bore 41 in the shaft 8.
  • the shaft 8 does not extend into the rotor cavity 31. It is connected to the rotor 4 at the pressure side.
  • the guide component 44 in the rotor cavity 31 has a section 84 with an enlarged diameter which, together with the inner wall of the cavity 31 in the rotor 4, forms the cooling gap 32.
  • a second section 85 which has a smaller diameter than section 84, penetrates the bore 41 in the shaft 8.
  • Coolant supplied centrally via the blind bore 45 is introduced via a transverse bore 88 into two mutually opposite groove sections 89 into the cavity 31 (pressure side).
  • the coolant then flows through the cooling gap 32 and passes via the transverse bores 47 into a line section 89 located centrally in the guide component.
  • the two transverse bores 88 and 90 are aligned approximately perpendicular to one another ,
  • the transverse bore 90 opens into mutually opposite groove sections 91 which are offset by approximately 90 ° with respect to the groove sections 89. This makes it possible for the coolant to flow back through these groove sections 91 to the transverse bores 49 in the area of the transmission space 16.
  • the rotor 4 comprises two sections 4 ′, 4 ′′ with different screw pitches and with a cavity 31 ′ or 31 ′′ in each case.
  • the shaft 8 extends into the cavity 31 ′′ of the rotor section on the pressure side 4 '' and thus forms the cooling gap 32 ''.
  • the guide component 44 is designed similarly to the embodiment according to FIGS. 5, 6. It has a section 84 with an enlarged diameter, which is located in the cavity 31 'of the rotor section 4' and, together with the inner wall of this rotor section 4 ', the cooling gap 32 'forms.
  • Another section 85 of the guide component 44 with a smaller diameter passes through the central bore 41 in the shaft 8.
  • the guide component 44 is provided with a central bore 45 which extends to the suction side of the rotor 4.

Landscapes

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

Abstract

L'invention concerne une pompe à vide à vis pourvue de deux arbres (7, 8) portant chacun un rotor (3, 4) présentant une cavité (31). Dans chaque cavité (31) se trouve une autre cavité (32) faisant partie d'un circuit de réfrigérant. Les arbres (7, 8) présentent des alésages (41) ouverts vers le côté refoulement, par lesquels se font l'amenée et l'évacuation du réfrigérant vers ou depuis les autres cavités (32). L'invention vise à améliorer l'efficacité du refroidissement des rotors. A cet effet, des éléments de guidage (44) servant au guidage séparé du réfrigérant entrant et sortant se trouvent dans les alésages ouverts (41) des arbres (7, 8).
EP00983238A 1999-12-27 2000-12-07 Pompe a vide a vis refroidie Expired - Lifetime EP1242742B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19963171A DE19963171A1 (de) 1999-12-27 1999-12-27 Gekühlte Schraubenvakuumpumpe
DE19963171 1999-12-27
PCT/EP2000/012318 WO2001048383A1 (fr) 1999-12-27 2000-12-07 Pompe a vide a vis refroidie

Publications (2)

Publication Number Publication Date
EP1242742A1 true EP1242742A1 (fr) 2002-09-25
EP1242742B1 EP1242742B1 (fr) 2006-08-16

Family

ID=7934616

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00983238A Expired - Lifetime EP1242742B1 (fr) 1999-12-27 2000-12-07 Pompe a vide a vis refroidie

Country Status (5)

Country Link
US (1) US20050069446A1 (fr)
EP (1) EP1242742B1 (fr)
JP (1) JP4800542B2 (fr)
DE (2) DE19963171A1 (fr)
WO (1) WO2001048383A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9624927B2 (en) 2010-12-14 2017-04-18 Gebr. Becker Gmbh Vacuum pump

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10039006A1 (de) * 2000-08-10 2002-02-21 Leybold Vakuum Gmbh Zweiwellenvakuumpumpe
DE10156179A1 (de) 2001-11-15 2003-05-28 Leybold Vakuum Gmbh Kühlung einer Schraubenvakuumpumpe
DE10156180B4 (de) * 2001-11-15 2015-10-15 Oerlikon Leybold Vacuum Gmbh Gekühlte Schraubenvakuumpumpe
WO2003048579A2 (fr) 2001-12-04 2003-06-12 Kag Holding A/S Pompe a vis pour le transport d'emulsions pouvant subir une manipulation mecanique
WO2006024818A1 (fr) * 2004-09-02 2006-03-09 The Boc Group Plc Refroidissement de rotors de pompe
DE102005012040A1 (de) * 2005-03-16 2006-09-21 Gebr. Becker Gmbh & Co Kg Rotor und Schraubenvakuumpumpe
GB0510892D0 (en) * 2005-05-27 2005-07-06 Boc Group Plc Vacuum pump
BE1017371A3 (nl) * 2006-11-23 2008-07-01 Atlas Copco Airpower Nv Rotor en compressorelement voorzien van zulke rotor.
US20090129956A1 (en) * 2007-11-21 2009-05-21 Jean-Louis Picouet Compressor System and Method of Lubricating the Compressor System
US9032871B1 (en) 2009-07-29 2015-05-19 Larry E. Koenig System and method for adjusting and cooling a densifier
JP5138662B2 (ja) * 2009-11-06 2013-02-06 株式会社神戸製鋼所 蒸気圧縮機
US8851409B2 (en) 2010-12-09 2014-10-07 Mark E. Koenig System for crushing
CA2728377C (fr) 2010-12-09 2014-12-02 Komar Industries, Inc. Procede et systeme de broyage
US9403336B2 (en) 2010-12-09 2016-08-02 Mark E. Koenig System and method for crushing and compaction
CN102192151A (zh) * 2011-05-19 2011-09-21 台州市星光真空设备制造有限公司 内冷式真空泵
KR101064152B1 (ko) 2011-06-20 2011-09-15 주식회사 에스백 직접 냉각 스크루식 진공펌프
US9586770B2 (en) 2011-08-05 2017-03-07 Mark E. Koenig Material waste sorting system and method
US9132968B2 (en) * 2011-11-04 2015-09-15 Mark E. Koenig Cantilevered screw assembly
US9346624B2 (en) 2011-11-04 2016-05-24 Mark E. Koenig Cantilevered screw assembly
EP2615307B1 (fr) * 2012-01-12 2019-08-21 Vacuubrand Gmbh + Co Kg Pompe à vide à vis
DE102013009040B4 (de) * 2013-05-28 2024-04-11 Ralf Steffens Spindelkompressor mit hoher innerer Verdichtung
US9821962B2 (en) 2015-12-14 2017-11-21 Mark E. Koenig Cantilevered screw assembly
CN106762668B (zh) * 2017-03-07 2018-06-22 北京艾岗科技有限公司 一种立式真空泵自循环润滑冷却系统
CN108869295A (zh) * 2018-08-02 2018-11-23 中船重工重庆智能装备工程设计有限公司 干式螺杆真空泵的散热系统
IT201800010291A1 (it) * 2018-11-13 2020-05-13 Tt Italy S P A Testa di miscelazione
CN112012931B (zh) * 2020-09-04 2022-05-24 浙江思科瑞真空技术有限公司 一种泵转子的冷却方法
CN114393811A (zh) * 2022-01-21 2022-04-26 玉环楚港模具科技有限公司 一种长滴管吹塑模具

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9624927B2 (en) 2010-12-14 2017-04-18 Gebr. Becker Gmbh Vacuum pump

Also Published As

Publication number Publication date
EP1242742B1 (fr) 2006-08-16
DE50013338D1 (de) 2006-09-28
DE19963171A1 (de) 2001-06-28
WO2001048383A1 (fr) 2001-07-05
JP4800542B2 (ja) 2011-10-26
US20050069446A1 (en) 2005-03-31
JP2003518588A (ja) 2003-06-10

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