US20050069446A1 - Cooled screw vacuum pump - Google Patents

Cooled screw vacuum pump Download PDF

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Publication number
US20050069446A1
US20050069446A1 US10/169,329 US16932902A US2005069446A1 US 20050069446 A1 US20050069446 A1 US 20050069446A1 US 16932902 A US16932902 A US 16932902A US 2005069446 A1 US2005069446 A1 US 2005069446A1
Authority
US
United States
Prior art keywords
coolant
pump according
rotor
hollow chamber
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.)
Abandoned
Application number
US10/169,329
Other languages
English (en)
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
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 filed Critical Leybold Vakuum GmbH
Assigned to LEYBOLD VAKUUM GMBH reassignment LEYBOLD VAKUUM GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KRIEHN, HARTMUT
Publication of US20050069446A1 publication Critical patent/US20050069446A1/en
Abandoned 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
    • 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 present invention relates to a screw vacuum pump, comprising two shafts, each bearing a rotor containing a hollow chamber. Said chamber contains a second hollow chamber which embodies a component of a coolant circuit.
  • the shafts have open bores on the delivery side, through which the coolant is supplied and evacuated to or from the additional hollow chambers.
  • a screw vacuum pump having these features is known from DE-A-198 20 523 (drawing FIG. 4 ).
  • the coolant is injected into the bores in the shafts, said bores being open on the delivery side.
  • the shafts are equipped with radial bores, through which the coolant enters into the hollow chambers in the rotor.
  • the outside walls of these hollow chambers are designed to be conical, widening in the direction of the delivery side.
  • the coolant film forming on the outside walls flows in the direction of the delivery side.
  • Via radial bores in the shaft on the delivery side the hot coolant returns through the respective central bore in the shaft and flows through these bores back to the respective opening.
  • the central shaft bore for accommodating the guide component may have a relatively large diameter.
  • Such a bore can be manufactured in the shaft material in a significantly easier manner compared to individual deep bore holes for the supply and evacuation channels.
  • guide components will allow cooling of the rotors in a “counterflow”, since even trouble-free crossing of the supplied and evacuated coolant flows can be arranged.
  • Cooling the rotors in a counterflow offers the additional advantage of a more even temperature distribution, so that the slots between rotor and casing can be maintained small and uniform.
  • the guide components allow cooling of the rotors in such a manner that all lines, slots, chambers or alike which are located within the rotor chambers and through which the coolant flows, are filled at all times completely with the flowing coolant. The effectivity of the cooling arrangement is thus considerably improved.
  • the screw vacuum pump 1 depicted in drawing FIG. 1 comprises pump chamber casing 2 with the rotors 3 and 4 .
  • Inlet 5 and outlet 6 of the pump 1 are schematically marked by arrows.
  • the rotors 3 and 4 are affixed on to the shafts 7 and 8 respectively, said shafts being each supported by two bearings 11 , 12 and 13 , 14 respectively.
  • One bearing pair 11 , 13 is located in a bearing plate 15 which separates the pump chamber being free of lubricant from a gear chamber 16 .
  • the second bearing pair 12 , 14 is located within pump chamber casing 2 .
  • the gear chamber 16 Located in casing 17 of the gear chamber 16 are the synchronising toothed wheels 18 , 19 affixed to the shafts 7 and 8 , as well as a pair of toothed wheels 21 , 22 serving the purpose of driving the pump 1 , where one toothed wheel is coupled to the shaft of the drive motor 23 arranged vertically besides the pump 1 .
  • the gear chamber has the function of an oil sump 20 .
  • the ends of the shafts 7 , 8 on the side of the gear chamber penetrate through bores 24 , 25 in the bottom of the gear chamber casing 17 and end in an oil containing chamber 26 being formed by casing 17 and a thereto affixed trough 27 .
  • the oil sump 16 is separated from the oil containing chamber 26 by seals 28 , 29 .
  • the second pair of bearings 12 , 14 is located in the area of the bores 24 , 25 .
  • the rotors 3 and 4 each have a hollow chamber 31 in which the shaft 8 extends and in which a further chamber 32 is present through which coolant flows. Since only rotor 4 is depicted by way of a partial section, the present invention is explained only with reference to this rotor 4 .
  • the chamber 32 through which the coolant flows is designed by way of a section of an annular gap and is located directly between shaft 8 (resp. 7) and rotor 4 (resp. 3).
  • the cylindrical inner wall of the rotor containing the hollow chamber 31 is equipped in its middle area with a section 33 turned off on a lathe, the depth of which corresponds to the thickness of the cooling slot 32 .
  • the shaft 8 rests flush against the inner wall of the hollow chamber 31 .
  • the cooling slot 32 is supplied with the coolant through the shaft 8 . It is equipped with a central bore 41 extending from the bottom end of the shaft 8 to the end of the cooling slot 32 on the delivery side. It forms a chamber 43 in which a guide component 44 for the coolant is located.
  • the guide component 44 extends from the bottom end of the shaft 8 up to and over the end of the cooling slot 32 on the delivery side.
  • the coolant is supplied via the longitudinal bore 45 in the guide component 44 , said bore being linked via truly aligned cross bores 46 through the component 44 and the shaft 8 to the end of the cooling slot 32 on the delivery side.
  • the shaft 8 is equipped with one or several cross bores 47 which open out into the chamber 43 formed by the pocket hole 41 and the face side of the guide component 44 .
  • Said chamber is linked via the longitudinal bore 48 and the truly aligned cross bores 49 (in the guide component 44 and in the shaft 8 ) to the gear chamber 16 .
  • the coolant is supplied from the oil containing chamber 26 through bores 45 and 46 into the cooling slot 32 .
  • the coolant flows through the cooling slot 32 from the delivery side to the suction side of the rotor 4 . Since most of the heat which needs to be dissipated is generated on the delivery side of the rotor 4 , the rotor 4 is cooled in a counterflow.
  • the coolant is evacuated initially through the second bore 47 in the chamber 43 in the shaft 8 as well as through the bores 48 , 49 .
  • the bore 48 extends from the suction side of the cooling slot 32 up to the level of the gear chamber 16 .
  • the cross bore 48 provides the link between bore 43 and the gear chamber 16 .
  • the gear chamber 16 resp. the oil sump 20 is linked to the chamber 26 through a line 51 in which there is located besides a cooler 52 and a filter 53 , an oil pump 54 which may be designed by way of a gear pump, for example.
  • the oil pump 54 ensures that the coolant enters at the necessary pressure and free of cavitation from chamber 26 into the bore 41 .
  • the guide component 44 comprises three sections 61 , 62 , 63 which divide the hollow chamber in the shaft 8 in to three partial chambers 64 , 65 , 43 which are each located at the level of the cross bores 49 , 46 and 47 .
  • the guide component 44 comprises three sections 61 , 62 , 63 which divide the hollow chamber in the shaft 8 in to three partial chambers 64 , 65 , 43 which are each located at the level of the cross bores 49 , 46 and 47 .
  • suitable bores in the sections 61 to 63 as well as line sections 67 and 68 linking said bores separate supply and evacuation of the coolant may be implemented.
  • the coolant is supplied through the bore 45 , which in contrast to the embodiments in accordance with drawing FIGS. 1 and 2 centrally penetrates the guide component 44 .
  • the oil pumped by a centrifugal pump 71 into the bore 45 enters into the hollow space 43 formed by the pocket hole 41 as well as the guide component 44 , and through the cross bore 46 into the chamber 32 through which the coolant flows.
  • the chamber 32 through which the coolant flows has the shape of an annular chamber of a relatively large volume being formed by the shaft 8 and the inner wall of the hollow chamber 31 .
  • this inner wall is designed to be conical in such a manner that the rotor's hollow chamber 31 widens conically in the direction of the delivery side of the rotors 3 , 4 , the coolant injected from the bores 46 into the chamber 32 is conveyed in the direction of the rotor's delivery side. Bubble- or cavitation-free operation of the coolant circuit is not required.
  • the coolant can be so metered that it will flow along the inner wall of the rotor's hollow chamber 31 by way of a thin film, for example.
  • the evacuation bores 47 are linked to lateral side channels 72 (or a section turned off on a lathe) in guide component 44 whereby said evacuation bores extend at the level of the bearing plate 15 up to the gear chamber 16 where they are linked to the cross bores 49 .
  • the embodiment in accordance with drawing 4 differs from the embodiments detailed above in that a bore is provided fully penetrating the shaft 8 and the rotor 4 .
  • a cover 76 is provided on the suction side, this cover being linked via a bolt 77 with the guide component 44 .
  • the guide component 44 is firmly inserted from the suction side. Together with bolt 77 and the cover 76 it serves the purposes of axially affixing the rotor 4 .
  • bore 41 On the delivery side, bore 41 has a smaller diameter.
  • the shaft 8 is equipped with an outer sleeve 77 which together with the inner wall of the hollow chamber 31 in the rotor 4 forms the cooling slot 32 1) .
  • This slot extends substantially only at the level of the delivery side of the rotor 4 . Radially displacing the cooling slot 32 towards the outside improves the cooling effect.
  • the coolant is only supplied through relatively short sections of longitudinal grooves 78 (or a section turned off on a lathe, annular channel) in the guide component 44 up to the cross bores 46 which penetrate the shaft 8 and the sleeve 77 .
  • the shaft 8 does not extend into the rotor's hollow chamber 31 .
  • Said shaft is linked to the rotor 4 at the level of the delivery side.
  • the guide component 44 in the rotor's hollow space 31 has a section 84 with an increased diameter which together with the inner wall of the hollow chamber 31 in rotor 4 forms the cooling slot 32 .
  • a second section 85 having, compared to the section 84 a smaller diameter, penetrates the bore 41 in the shaft 8 .
  • Coolant supplied 3) centrally through the pocket hole 45 enters through a cross bore 88 into two groove sections 89 facing each other and then the coolant enters into the hollow chamber 31 (delivery side). Thereafter the coolant flows through the cooling slot 32 and enters through cross bores 47 into a line section 89 located centrally in the guide component. Said line section extends to a second cross bore 90 placed on the suction side with respect to the first cross bore 88 .
  • the two cross bores 88 and 90 are arranged approximately perpendicular to each other.
  • the cross bore 90 2 Translator's note: The German text states “ . . . nach den FIG. 5 a occidentalreckt . . . ” here whereas “ . . . nach den FIG. 5 a und 5 b occidentalreckt . . . ” would make for a correct sentence. Therefore the latter has been assumed for the translation.
  • the rotor 4 comprises two sections 4 ′ and 4 ′′ having differently designed threads as well as each with a hollow chamber 31 ′ and 31 ′′ respectively.
  • the shaft 8 extends into the hollow chamber 31 ′′ of the rotor section on the delivery side 4 ′′ and thus forms the cooling slot 32 ′′.
  • the guide component 44 is similarly designed as in the embodiment in accordance with drawing FIGS. 5, 6 . It has a section 84 with an increased diameter which is located in hollow chamber 31 ′ of the rotor section 4 ′ and which forms together with the inside wall of this rotor section 4 ′ the cooling slot 32 ′.
  • a further section 85 of the guide component 44 having a smaller diameter penetrates the central bore 41 in shaft 8 .
  • the guide component 44 is equipped with a central bore 45 extending to the suction side of the rotor 4 .
  • cooling slot 32 ′′ on the suction side so that the coolant passes sequentially through the two cooling slots 32 ′, 32 ′′.
  • evacuation opening 47 ′′ on the delivery side of the cooling slot 32 ′′ is linked to the evacuation opening 49 at the level of the gear chamber 16 .
  • guide component 44 as a tie rod, specifically for affixing the rotor section 4 ′.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US10/169,329 1999-12-27 2000-12-07 Cooled screw vacuum pump Abandoned US20050069446A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19963171A DE19963171A1 (de) 1999-12-27 1999-12-27 Gekühlte Schraubenvakuumpumpe
DE19963171.9 1999-12-27
PCT/EP2000/012318 WO2001048383A1 (de) 1999-12-27 2000-12-07 Gekühlte schraubenvakuumpumpe

Publications (1)

Publication Number Publication Date
US20050069446A1 true US20050069446A1 (en) 2005-03-31

Family

ID=7934616

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/169,329 Abandoned US20050069446A1 (en) 1999-12-27 2000-12-07 Cooled screw vacuum pump

Country Status (5)

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

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060269424A1 (en) * 2005-05-27 2006-11-30 Michael Henry North Vacuum pump
US20080031761A1 (en) * 2004-09-02 2008-02-07 North Michael H Cooling of Pump Rotors
US20090129956A1 (en) * 2007-11-21 2009-05-21 Jean-Louis Picouet Compressor System and Method of Lubricating the Compressor System
US20100054980A1 (en) * 2006-11-23 2010-03-04 Moens Erik Eric Daniel Rotor and compressor element provided with such rotor
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
DE102010061202A1 (de) 2010-12-14 2012-06-14 Gebr. Becker Gmbh Vakuumpumpe
CN103256224A (zh) * 2012-01-12 2013-08-21 维科普兰德有限两合公司 用于螺旋真空泵的螺旋转子
US8708266B2 (en) 2010-12-09 2014-04-29 Mark E. Koenig System for crushing with screw porition that increases in diameter
US8720805B1 (en) 2009-07-29 2014-05-13 Larry E. Koenig System and method for cooling a densifier
US8851409B2 (en) 2010-12-09 2014-10-07 Mark E. Koenig System for crushing
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
US9403336B2 (en) 2010-12-09 2016-08-02 Mark E. Koenig System and method for crushing and compaction
US9586770B2 (en) 2011-08-05 2017-03-07 Mark E. Koenig Material waste sorting system and method
CN106762668A (zh) * 2017-03-07 2017-05-31 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
US9821962B2 (en) 2015-12-14 2017-11-21 Mark E. Koenig Cantilevered screw assembly
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
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

Families Citing this family (9)

* 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
DE10156180B4 (de) 2001-11-15 2015-10-15 Oerlikon Leybold Vacuum Gmbh Gekühlte Schraubenvakuumpumpe
DE10156179A1 (de) 2001-11-15 2003-05-28 Leybold Vakuum Gmbh Kühlung einer Schraubenvakuumpumpe
US7165933B2 (en) 2001-12-04 2007-01-23 Kag Holding A/S Screw pump for transporting emulsions susceptible to mechanical handling
DE102005012040A1 (de) * 2005-03-16 2006-09-21 Gebr. Becker Gmbh & Co Kg Rotor und Schraubenvakuumpumpe
JP5138662B2 (ja) * 2009-11-06 2013-02-06 株式会社神戸製鋼所 蒸気圧縮機
KR101064152B1 (ko) * 2011-06-20 2011-09-15 주식회사 에스백 직접 냉각 스크루식 진공펌프
DE102013009040B4 (de) * 2013-05-28 2024-04-11 Ralf Steffens Spindelkompressor mit hoher innerer Verdichtung
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

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US3531227A (en) * 1968-07-05 1970-09-29 Cornell Aeronautical Labor Inc Gear compressors and expanders
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US6045343A (en) * 1998-01-15 2000-04-04 Sunny King Machinery Co., Ltd. Internally cooling rotary compression equipment
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US6863511B2 (en) * 2000-08-10 2005-03-08 Leybold Vakuum Gmbh Two-shaft vacuum pump

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DE19800825A1 (de) * 1998-01-02 1999-07-08 Schacht Friedrich Trockenverdichtende Schraubenspindelpumpe
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US3405604A (en) * 1965-05-14 1968-10-15 Lysholm Alf Method of driving a screw engine power unit and a power unit to be driven according to such method
US3531227A (en) * 1968-07-05 1970-09-29 Cornell Aeronautical Labor Inc Gear compressors and expanders
US3796526A (en) * 1972-02-22 1974-03-12 Lennox Ind Inc Screw compressor
US5292237A (en) * 1990-10-08 1994-03-08 Kabushiki Kaisha Kobe Seiko Sho Melt pump
US5924855A (en) * 1995-06-21 1999-07-20 Sihi Industry Consult Gmbh Screw compressor with cooling
US6544020B1 (en) * 1997-10-10 2003-04-08 Leybold Vakuum Gmbh Cooled screw vacuum pump
US6045343A (en) * 1998-01-15 2000-04-04 Sunny King Machinery Co., Ltd. Internally cooling rotary compression equipment
US6758660B2 (en) * 1999-12-27 2004-07-06 Leybold Vakuum Gmbh Screw vacuum pump with a coolant circuit
US6394777B2 (en) * 2000-01-07 2002-05-28 The Nash Engineering Company Cooling gas in a rotary screw type pump
US6422844B2 (en) * 2000-04-28 2002-07-23 Hitachi Air Conditioning Systems Co., Ltd. Screw compressor
US6863511B2 (en) * 2000-08-10 2005-03-08 Leybold Vakuum Gmbh Two-shaft vacuum pump

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7963744B2 (en) * 2004-09-02 2011-06-21 Edwards Limited Cooling of pump rotors
US20080031761A1 (en) * 2004-09-02 2008-02-07 North Michael H Cooling of Pump Rotors
US20060269424A1 (en) * 2005-05-27 2006-11-30 Michael Henry North Vacuum pump
US8192186B2 (en) * 2006-11-23 2012-06-05 Atlas Copco Airpower, Naamloze Vennootschap Rotor having a cooling channel and compressor element provided with such rotor
US20100054980A1 (en) * 2006-11-23 2010-03-04 Moens Erik Eric Daniel Rotor and compressor element provided with such rotor
US20090129956A1 (en) * 2007-11-21 2009-05-21 Jean-Louis Picouet Compressor System and Method of Lubricating the Compressor System
US8720330B1 (en) 2009-07-29 2014-05-13 Larry E. Koenig System and method for adjusting and cooling a densifier
US9032871B1 (en) 2009-07-29 2015-05-19 Larry E. Koenig System and method for adjusting and cooling a densifier
US8726804B1 (en) 2009-07-29 2014-05-20 Larry E. Koenig System and method for adjusting and cooling a densifier
US8720805B1 (en) 2009-07-29 2014-05-13 Larry E. Koenig System and method for cooling a densifier
US10081148B2 (en) 2010-12-09 2018-09-25 Mark E. Koenig System and method for crushing and compaction
US9403336B2 (en) 2010-12-09 2016-08-02 Mark E. Koenig System and method for crushing and compaction
US8851409B2 (en) 2010-12-09 2014-10-07 Mark E. Koenig System for crushing
US8708266B2 (en) 2010-12-09 2014-04-29 Mark E. Koenig System for crushing with screw porition that increases in diameter
WO2012080034A2 (de) 2010-12-14 2012-06-21 Gebr. Becker Gmbh Vakuumpumpe
DE102010061202A1 (de) 2010-12-14 2012-06-14 Gebr. Becker Gmbh Vakuumpumpe
JP2013545932A (ja) * 2010-12-14 2013-12-26 ゲーエーベーエル．ベッケル・ゲーエムベーハー 真空ポンプ
CN103261694A (zh) * 2010-12-14 2013-08-21 格布尔.贝克尔有限责任公司 真空泵
US9624927B2 (en) 2010-12-14 2017-04-18 Gebr. Becker Gmbh Vacuum pump
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
US9586770B2 (en) 2011-08-05 2017-03-07 Mark E. Koenig Material waste sorting system and method
US10640309B2 (en) 2011-08-05 2020-05-05 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
US9815636B2 (en) 2011-11-04 2017-11-14 Mark E. Koenig Cantilevered screw assembly
US9212005B1 (en) * 2011-11-04 2015-12-15 Mark E. Koenig Cantilevered screw assembly
CN103256224A (zh) * 2012-01-12 2013-08-21 维科普兰德有限两合公司 用于螺旋真空泵的螺旋转子
US9821962B2 (en) 2015-12-14 2017-11-21 Mark E. Koenig Cantilevered screw assembly
CN106762668A (zh) * 2017-03-07 2017-05-31 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
WO2020100005A1 (en) * 2018-11-13 2020-05-22 Tt Italy S.P.A. Mixing head
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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JP4800542B2 (ja) 2011-10-26
DE50013338D1 (de) 2006-09-28
EP1242742A1 (de) 2002-09-25
JP2003518588A (ja) 2003-06-10
EP1242742B1 (de) 2006-08-16
DE19963171A1 (de) 2001-06-28

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