WO2009040412A1 - Pompe a vide a deux rotors helicoïdaux - Google Patents
Pompe a vide a deux rotors helicoïdaux Download PDFInfo
- Publication number
- WO2009040412A1 WO2009040412A1 PCT/EP2008/062904 EP2008062904W WO2009040412A1 WO 2009040412 A1 WO2009040412 A1 WO 2009040412A1 EP 2008062904 W EP2008062904 W EP 2008062904W WO 2009040412 A1 WO2009040412 A1 WO 2009040412A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rotor
- pump
- equipment
- transverse
- outlet
- Prior art date
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
- 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
- F04C18/126—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 radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots 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
- F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
- F04C25/02—Adaptations of pumps for special use of pumps for elastic fluids for producing high vacuum
-
- 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
- F04C2240/40—Electric motor
- F04C2240/402—Plurality of electronically synchronised motors
Definitions
- the present invention relates to pumping devices capable of generating and maintaining a suitable vacuum in equipment.
- Generating and maintaining a vacuum in equipment is commonly used in industrial semiconductor manufacturing processes, with certain manufacturing steps to be performed under vacuum.
- the equipment is connected to a pumping device that lowers the internal pressure of the equipment to a suitable vacuum.
- the known pumping devices generally comprise at least one primary pump, placed at the discharge of the vacuum line, and at least one secondary pump connected in series in the flow path of the gas pumped between the primary pump and the pump. equipment.
- a first known pumping device is used for applications requiring that the pressure in the equipment be within a pressure range of about 10 -2 mbar to about 10 mbar, and then a secondary ROOTS pump is usually used.
- This ROOTS pump is connected to the primary pump suction and is typically used for rapid pumping of large volume equipment or process streams.
- ROOTS pumps have two parallel bean cross section rotors defining intermeshing lobes.
- the suction and discharge ports are radial, perpendicular to the axes of rotation of the rotors.
- the pumping devices thus formed are bulky and heavy, and are important generators of vibrations and noise.
- the industrialists deport the pumping unit away from the equipment using pipes easily reaching several meters in length.
- these lines must have a high conductance. They are therefore large and bulky and their interior volume is added to that of the equipment: the pumping system is therefore less reactive because it has to pump a large volume to establish the internal gas pressure in the equipment.
- it is sometimes necessary to maintain the gases at high temperature inside the vacuum line (particular chemistries with gas to be maintained in volatile form with high temperatures up to 150 0 C). These pumping groups then require expensive heaters to keep these large pipes at high temperatures.
- ROOTS pumps with radial input and output always generate vibrations and noise.
- ROOTS pumps normally used in position in which the axes of the rotors are horizontal, have the disadvantage of being very cumbersome on the ground.
- secondary pumps of the molecular or turbomolecular type may be used, however this type of pump can not be used for applications requiring the heating of gases in the pumping device and / or in higher-pressure applications
- Industrialists continually want to reduce the size and cost of equipment in their manufacturing rooms, particularly in the semiconductor industry, where cleanroom space is very expensive. The chemistries, too, evolve and require the pumping devices to always be more efficient in terms of pumping rate. These new criteria of size and flow require to find new pumping devices less cumbersome and less expensive, clean and at high pumping rate.
- the problem proposed by the present invention is to design a vacuum pump with high pumping rate, which can be used as a secondary pump, and sufficiently compact, low noise and low pollution for it can be placed in the immediate vicinity of the equipment without disrupting its operation.
- the vacuum pump of the invention will also be able to pump powders as well as other particles generated in the equipment.
- the invention provides a more responsive pumping system for the efficient generation and maintenance of a vacuum in equipment.
- the invention provides a vacuum pump in which:
- an envelope defines two parallel cylindrical chambers transversely overlapping, limited by cylindrical peripheral surfaces and transverse end surfaces, and having respective axes defining a longitudinal direction, the transverse end surfaces defining a transverse direction,
- an inlet passage and an outlet passage pass through the envelope in two respective positions, these positions being generally opposite,
- two rotors are each rotatably disposed in a respective cylindrical chamber, the rotors having lobed complementary lobe rotor bodies and rotor shafts, each lobe of each rotor having a radial bearing surface cooperating sealingly with the cylindrical peripheral surface of the respective cylindrical chamber, the rotor bodies having first and second transverse bearing surfaces each sealingly cooperating with a respective transverse end surface of a chamber,
- each rotor body has a helical twist around a longitudinal axis between the first transverse bearing surface and the second transverse bearing surface
- the inlet passage communicates with the interior of the envelope via an inlet orifice provided in the first transverse end surface
- each rotor is held cantilevered by rotor guide means situated in downstream of the rotor body in the direction of flow of the pumped fluid, the pump being devoid of rotor guide means upstream of the rotor bodies.
- each of the two rotor bodies has a ROOTS type transverse profile, and is designed with a quarter-turn helical twist between the first rotor transverse bearing surface and the second rotor transverse bearing surface.
- the inlet orifice being located along a first side of the plane defined by the axes of the rotors, and the outlet orifice being located along a second side of the plane defined by the axes of the rotors.
- This quarter-turn helical twist provides the best compromise between rotor diameter.
- a pumping rate of about 4000 m 3 / h can be achieved.
- control and supply means for controlling the speed of rotation of the rotors.
- the pumping rate and the upstream pressure can then be easily adjusted according to the equipment and the processing steps.
- the single-stage vacuum pump thus formed has the advantages of ROOTS pumps or screw pumps, ie a large pumping rate. Its special design also gives it the advantage of generating less vibrations and fewer noises, and having a large flow rate at a smaller volume thanks to the possibility of faster rotation. Its design also avoids the generation of retrograde particulate pollution in adjacent equipment, since the pumped particles enter the pump axially through the inlet passageway and are not likely to be returned to the equipment by rebound on rotor portions. upstream movement. Its design also avoids retrograde pollution due to the absence of bearings and lubricants in the low pressure zone upstream of the rotors.
- This vacuum pump can therefore be placed in the immediate vicinity of equipment in which it is desired to generate and maintain a vacuum, and can correctly fulfill the functions of secondary pump.
- the absence of mechanical guide elements of the upstream rotors leaves room for choosing the shape and position of the suction port of the pump which ensure in particular the best flow of the pump.
- the pump according to the invention comprises two rotor bodies each having lobes which have a cross section whose contour has a profile in conventional type ROOTS pumps. This profile provides the best compromise between the external size of the pump according to the invention and the flow rate of the order of 4000 m 3 / h that is desired.
- the rotor bodies may each comprise two lobes.
- each rotor body comprises at least three lobes.
- One advantage is a better dynamic balance, for the reduction of noise and vibrations.
- Another advantage is a better compression ratio.
- a disadvantage is a reduction in the pumping rate at the same size, and a greater complexity of machining.
- the vacuum pump of the invention may comprise means for maintaining it in a position in which the axes of the rotors are oriented, with respect to a vertical direction, at an orientation angle less than 90 °.
- the orientation angle may be chosen less than 45 ° with respect to the vertical. Such an angle can further reduce the footprint of the vacuum pump of the invention, and promotes the expulsion of particles.
- the particular design of the vacuum pump of the invention allows its use along the vertical axis. Congestion is then minimum.
- the vacuum pump according to the invention may comprise means for maintaining it in a position in which the inlet orifice is higher than the outlet orifice.
- the vacuum pump according to the invention is made from materials which are selected to withstand up to a temperature of about 150 ° C.
- the choice of materials makes it possible to use the vacuum pump of the invention at the temperatures usually required to make certain gases volatile in the vacuum lines.
- Such a temperature can also be achieved by a judicious choice of the materials constituting the insulation part between the pumping part and the mechanical part of the pump.
- the vacuum pump comprises a motor mounted on one of the drive shafts between the guide means.
- the vacuum pump comprises two synchronized motors each mounted on a respective drive shaft between the guide means.
- the invention also provides a pumping system for generating and maintaining a vacuum in equipment, comprising:
- a primary pump having a primary suction inlet and a primary discharge outlet
- a secondary pump having a secondary suction inlet connected to an outlet of the equipment via an inlet pipe, and having a secondary discharge outlet connected to the primary suction inlet via an intermediate pipe, and which :
- the secondary pump is a single-stage pump of the type as defined above,
- the secondary pump is positioned in the immediate vicinity of the equipment
- the primary pump is remote from the equipment.
- the secondary suction inlet is disposed facing the outlet of the equipment, and the inlet pipe directly connects the secondary suction inlet to the outlet of the equipment.
- the inlet pipe can then be very short or non-existent.
- the single-stage vacuum pump as designed according to the present invention has the advantage of being positioned in the immediate vicinity of the equipment.
- the pipes are smaller than in the pumping devices of the prior art. Fewer pipelines means less space in the clean room, and less volume to pump, so more responsiveness to the pumping system.
- the pumping system comprises control and supply means for controlling the speed of the secondary pump.
- the control and supply means control the secondary pump so as to adjust its speed in a speed range allowing optimal control of the suction pressure by the discharge pressure.
- the pumping system further comprises a valve placed at the discharge of the secondary pump, and control and supply means for controlling the opening of the valve.
- the pumping system comprises a valve placed at the discharge of the secondary pump, the control and supply means acting on the speed of the secondary pump and / or on the opening of the valve so as to regulate the pressure in the equipment.
- FIG. 1 is a front view in longitudinal section in the plane of rotation axes of a pump according to an embodiment of the invention
- FIG. 2 is a front view of the pump of Figure 1, in partial longitudinal section along the plane of the axes of rotation;
- FIG. 3 is a top view in cross section along the plane C-C of Figure 1;
- FIG. 4 is a view from above of the pump of FIG. 1;
- FIG. 5 is a perspective view illustrating a pair of ROOTS transverse profile rotors according to one embodiment of the invention
- FIG. 6 is a front view of the pair of rotors of FIG. 5; and FIG. 7 is an overall diagram of a pumping system according to one embodiment of the invention.
- FIG. 1 which illustrates a vacuum pump according to one embodiment of the invention.
- This pump comprises a pump body in which there are two main parts.
- a first main part comprises the mechanical drive elements 19 of the pump of the invention.
- a second main portion comprises an envelope 1 sealingly enclosing the elements constituting the pump portion 22 of the pump.
- the first main part comprises a first drive shaft 21a and a second drive shaft 21b, parallel to each other.
- the two drive shafts 21a and 21b are held by bearings 29a, 29b, 29c and 29d.
- a motor rotor 30 is attached to the second drive shaft 21b between the bearings 29c and 29d, and rotates in a fixed motor stator 31 in the pump body between said bearings 29c and 29d.
- Electrical conductors 20 supply the motor stator 31 with electrical energy to drive the second drive shaft 21b in rotation.
- the first drive shaft 21a defines a first axis 11 and the second drive shaft 21b defines a second axis M-11.
- a driving gear 32 is keyed on the second drive shaft 21b and meshes with a driven gear 33.
- This driven gear 33 is keyed to the first drive shaft 21a.
- the second main part comprises the envelope 1 which defines two parallel cylindrical chambers 2a and 2b, centered on the axes 1-1 and M-11, overlapping transversely. These parallel cylindrical chambers 2a and 2b are limited by cylindrical peripheral surfaces 3a and 3b and transverse end surfaces 10 and 12.
- An inlet passage 4 is adapted to be connected to equipment in which the vacuum must be made and to allow the fluids to enter the pump according to the invention.
- the inlet passage 4 communicates with the interior of the casing 1 via an inlet orifice 9 provided essentially in the first transverse end surface 10.
- Two parallel rotors A and B are each rotatably disposed in a respective cylindrical chamber 2a or 2b about a respective axis 11a or 11a.
- the rotors A and B each respectively have a rotor body 6a and 6b and a downstream coaxial shaft 62a and 62b.
- the rotor bodies 6a and 6b are axially limited by first coplanar transverse surface surfaces 7a and 7b and by coplanar second cross-surface bearing surfaces 8a and 8b.
- Each rotor A or B is fixed cantilevered respectively by its downstream coaxial shaft 62a or 62b, at the end of the first drive shaft 21a or the second drive shaft 21b of the first main portion.
- the rotors are held cantilevered by guide means (the bearings 29a-29d) located downstream of the rotor bodies 6a and 6b in the direction of flow of the pumped fluids. There is no guiding means in the zone of low gas pressure upstream of the rotor bodies 6a and 6b.
- the guide means 29a-29d may be plain bearings, or magnetic bearings, or gas bearings, for example.
- a thermally insulating wall 100 separates the first main portion from the second main portion. In this way, it is possible to heat the second main part which contains the pumped gases, in order to prevent their deposition on the pumping elements, while maintaining a lower temperature in the first main part provided with holding means and rotor drive.
- a motor for example consisting of a rotor 30 and a stator 31, can be mounted directly on one of the drive shafts 21a or 21b between two guide means 29a and 29b, or 29c and 29d. This makes it possible to increase the compactness of the pump with respect to a motor mounted at the end of the shaft after the gears.
- the vacuum pump according to the invention operates with two synchronized motors each mounted on a respective drive shaft 21a or 21b between the guide means. This allows to have more power in a given size.
- FIG. 2 in which the same essential elements are identified by the same numerical references as in FIG. 1.
- An outlet passage 5 passes through the envelope 1 and is positioned in such a way that the inlet passage 4 and the outlet passage 5 through the casing 1 in two respective positions generally opposite.
- the outlet passage 5 communicates with the inside of the casing 1 through an outlet orifice 1 1 provided in the second transverse end surface 12. It is easily seen that, on the pump according to the invention, the inlet and the fluid outlet is effected axially.
- FIG. 3 is a section along the plane CC of Figure 1.
- the same essential elements are identified by the same reference numerals as in Figures 1 and 2.
- the rotor A comprises a rotor body 6a having two opposing lobes 60a and 61a.
- the rotor B comprises a rotor body 6b having two opposing lobes 60b and 61b.
- the rotor bodies 6a and 6b are each rotatably disposed in a respective cylindrical chamber 2a and 2b.
- Each lobe 60a, 61a, 60b, 61b of each rotor body 6a and 6b has a respective radially extending surface 25a or 26a and 25b or 26b, cooperating sealingly with the cylindrical peripheral surface 3a or 3b of the chamber respective cylindrical 2a or 2b during a portion of the rotary stroke of the rotor A or B corresponding.
- the cross sections of the rotor bodies 6a and 6b have contours similar to the contours of the conventional ROOTS profiles.
- FIGS. 5 and 6 illustrate the pairs of rotor bodies 6a and 6b respectively in perspective and in plan view.
- each rotor body 6a and 6b has a helical twist about a respective longitudinal axis 11 or M-11 between the first transverse bearing surface 7a or 7b and the second transverse bearing surface 8a or 8b, the helical torsions of the rotors being in opposite directions.
- This helical twist of the ROOTS type rotor profiles makes it possible to have suction and discharge ports on the walls perpendicular to the axes and thus to have axial pumping.
- FIG. 4 also illustrates the offset between the inlet passage 4 and the outlet passage 5.
- each of the two rotor bodies 6a and 6b is designed with a quarter-turn helical twist between the first and second transverse bearing surfaces 7a, 7b, 8a and 8b.
- the inlet orifice 9 is located along a first side of the plane defined by the axes II and M-II of the rotor bodies 6a and 6b
- the outlet orifice 1 1 is located along the second side of the plane defined by the axes ll and M-II of the rotor bodies 6a and 6b.
- the bodies of rotors 6a and 6b illustrated in the figures are relatively short, their axial height H being less than or equal to their overall diameter D.
- the H / D ratio is less than 1, preferably about 0.6.
- the motor formed by the rotor 30 and the stator 31 is positioned on the second drive shaft 21b between the bearings 29c and 29d, increasing the compactness of the pump.
- the stator 31 is fed via the electrical conductors 20. This has the effect of rotating the second drive shaft 21b which rotates, via the gears 32 and 33, the first drive shaft 21a.
- the rotors A and B mechanically coupled to drive shafts 21a and 21b are then rotated in opposite directions from each other.
- the fluids to be pumped continuously enter the pump of the invention through the inlet orifice 9 and fill a volume between the rotor bodies 6a and 6b.
- the rotor bodies 6a and 6b while still rotating on themselves, move said volume filled with fluids towards the outlet orifice January 1.
- the fluid-filled volume is isolated from both the inlet port 9 and the outlet port 11.
- the fluid-filled volume is in connection with the outlet port 1 1, and the fluids are expelled.
- the pumping continues with the following volumes.
- the table below validates certain qualities of a single-stage vacuum pump of the invention compared to a conventional single-stage ROOTS type pump. This table compares the performance of the pump of the invention (I) compared to a conventional ROOTS type pump (R) of the same nominal flow, in terms of speed, dimensions, volume, weight and power.
- the pump of the invention is less bulky, has a much higher rotational speed, and its engine consumes less power.
- the design of the pump according to the invention makes it possible, compared to a conventional ROOTS pump of the same flow rate, to reduce the volume. of the pump by a factor of 4, its weight by a factor of 3 and its power consumption by a factor of about 2.
- the pump according to the invention can operate efficiently over a wide range of flow rates, for example from 1,000 m 3 / h to more than 4,000 m 3 / h by varying its speed of rotation and at low energy.
- the rotor bodies 6a and 6b have a helical twist of a quarter turn.
- a helical twist of different angular value thereby lengthening the rotors.
- Twisting a half turn would form a second intermediate fluid passage and would constitute a second pumping stage.
- the resultant pump would be two-stage.
- FIG. 7 illustrates the pumping system according to the invention.
- This system consists of equipment 13 in which it is desired to ensure an appropriate vacuum.
- An output 13a of the equipment 13 is connected to the secondary suction inlet 15a of a secondary pump 15 via an inlet pipe 16.
- the secondary pump 15 is of a type as described previously, with two rotors A and B ( Figure 1) helical twist.
- the secondary pump 15 has a discharge outlet 15b which is connected to the suction inlet 14a of a primary pump 14 via an intermediate pipe 17.
- the discharge outlet 14b of the primary pump 14 allows the system according to the invention to repress at atmospheric pressure.
- the secondary suction inlet 15a is disposed opposite the outlet of the equipment 13a, and the inlet pipe 16 directly connects the secondary suction inlet 15a to the outlet of the equipment 13a.
- the inlet pipe 16 is as short as possible, and may be non-existent in the case of a direct coupling of the secondary pump 15 to the equipment 13. This avoids the additional volumes to be pumped, and the losses of conductance due to pipes. It is then possible to further reduce the size of the secondary pump 15.
- the primary pump 14 is deported away from the equipment, for example outside the manufacturing room, while being connected to the pump. secondary 15 by a relatively long intermediate pipe 17, limiting the size of the pumping system in the manufacturing room, and avoiding disturbing the equipment 13 by vibration, noise, or other nuisance.
- the gas transferred to the exhaust is at a pressure 10 to 100 times higher than direct output of the process chamber, which allows to reduce the diameter of the pipelines transferring the process gases to the primary pump and therefore the cost of connection.
- the particle traps may be smaller and placed downstream of the secondary pump 15 instead of being at the chamber outlet, thus avoiding phenomena of retro-diffusion of particles in the process chamber.
- the removal of the intermediate lines between the equipment 13 and the secondary pump 15 reduces the costs of the connections, and reduces the power consumption.
- the rotational speed of the pump rotors A and B can be controlled by control and supply means 18 which supply electrical energy to the motor (30-31, FIG. 1) of the secondary pump 15 of the invention. Due to the position of the secondary pump 15 in the immediate vicinity of the equipment 13, a secondary pump speed variation 15 or a variation in pressure at its discharge quickly react on the equipment.
- control and supply means 18 can act on the speed of the secondary pump 15 so as to regulate the pressure in the equipment 13.
- a valve 40 can be provided placed at the discharge of the secondary pump 15.
- the control and supply means 18 then drive the opening of the valve 40, which modifies the discharge pressure.
- the modification of the discharge pressure causes the modification of the compression ratio of the pump and therefore the modification of the suction pressure, which itself is the pressure in the equipment 13.
- the control means and power supplies 18 can thus controlling the opening of the valve 40 so as to regulate the pressure in the equipment 13, for example. It is also possible to combine the two systems, rotational speed of the pump and discharge valve.
- control and supply means 18 control the secondary pump 15 so as to adjust its speed in a speed range allowing optimal control of the suction pressure by the discharge pressure, and the control means and feed 18 control the opening of the discharge valve 40 so as to control the suction pressure by the discharge pressure.
- EP-1 475 535 teaches how to control the secondary pump for this.
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010526301A JP2010540824A (ja) | 2007-09-26 | 2008-09-26 | 2つのヘリカルロータを備える真空ポンプ |
CN200880109072A CN101809290A (zh) | 2007-09-26 | 2008-09-26 | 具有两个螺旋形转子的真空泵 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0757858A FR2921444A1 (fr) | 2007-09-26 | 2007-09-26 | Pompe a vide a deux rotors helicoidaux. |
FR0757858 | 2007-09-26 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2009040412A1 true WO2009040412A1 (fr) | 2009-04-02 |
Family
ID=39387205
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2008/062904 WO2009040412A1 (fr) | 2007-09-26 | 2008-09-26 | Pompe a vide a deux rotors helicoïdaux |
Country Status (8)
Country | Link |
---|---|
EP (1) | EP2042739B1 (fr) |
JP (1) | JP2010540824A (fr) |
KR (1) | KR20100072289A (fr) |
CN (1) | CN101809290A (fr) |
AT (1) | ATE453801T1 (fr) |
DE (1) | DE602008000482D1 (fr) |
FR (1) | FR2921444A1 (fr) |
WO (1) | WO2009040412A1 (fr) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103062046A (zh) * | 2013-01-07 | 2013-04-24 | 艾迪机器(杭州)有限公司 | 扭曲式转子泵 |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013112704B4 (de) | 2013-11-18 | 2022-01-13 | Pfeiffer Vacuum Gmbh | Gehäuse für eine Wälzkolbenpumpe |
CN108953177B (zh) * | 2018-07-27 | 2020-03-31 | 东北大学 | 一种用于提高涡轮分子泵抽气速率的过渡结构 |
FR3103862B1 (fr) * | 2019-12-03 | 2021-12-03 | Pfeiffer Vacuum | Rotor et pompe à vide sèche multiétagée |
BR112022008743A2 (pt) * | 2019-12-04 | 2022-07-26 | Ateliers Busch S A | Sistema de bombeamento redundante e método de bombeamento por meio deste sistema de bombeamento |
FR3118650B1 (fr) | 2021-01-05 | 2023-03-24 | Pfeiffer Vacuum | Etage de pompage et pompe à vide sèche |
GB2607936A (en) * | 2021-06-17 | 2022-12-21 | Edwards Ltd | Screw-type vacuum pump |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB809443A (en) * | 1954-02-27 | 1959-02-25 | Heraeus Gmbh W C | Improvements in or relating to rotary high-vacuum pumps |
US5118268A (en) * | 1991-06-19 | 1992-06-02 | Eaton Corporation | Trapped volume vent means with restricted flow passages for meshing lobes of roots-type supercharger |
DE19522551A1 (de) * | 1995-06-21 | 1997-01-02 | Sihi Ind Consult Gmbh | Zweiwellen-Verdrängermaschine |
DE19522557A1 (de) * | 1995-06-21 | 1997-01-02 | Sihi Ind Consult Gmbh | Drehkolbenverdichter, insbesondere Vakuumpumpe |
US6129534A (en) * | 1999-06-16 | 2000-10-10 | The Boc Group Plc | Vacuum pumps |
DE102005017575A1 (de) * | 2004-08-05 | 2006-03-16 | Börger GmbH | Drehkolbenpumpe mit einem Pumpengehäuse und zwei zweiflügeligen Drehkolben |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2854667B1 (fr) | 2003-05-09 | 2006-07-28 | Cit Alcatel | Controle de pression dans la chambre de procedes par variation de vitesse de pompes, vanne de regulation et injection de gaz neutre |
-
2007
- 2007-09-26 FR FR0757858A patent/FR2921444A1/fr not_active Withdrawn
-
2008
- 2008-09-26 DE DE602008000482T patent/DE602008000482D1/de active Active
- 2008-09-26 WO PCT/EP2008/062904 patent/WO2009040412A1/fr active Application Filing
- 2008-09-26 KR KR1020107008932A patent/KR20100072289A/ko not_active Application Discontinuation
- 2008-09-26 JP JP2010526301A patent/JP2010540824A/ja active Pending
- 2008-09-26 CN CN200880109072A patent/CN101809290A/zh active Pending
- 2008-09-26 AT AT08165208T patent/ATE453801T1/de not_active IP Right Cessation
- 2008-09-26 EP EP08165208A patent/EP2042739B1/fr not_active Not-in-force
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB809443A (en) * | 1954-02-27 | 1959-02-25 | Heraeus Gmbh W C | Improvements in or relating to rotary high-vacuum pumps |
US5118268A (en) * | 1991-06-19 | 1992-06-02 | Eaton Corporation | Trapped volume vent means with restricted flow passages for meshing lobes of roots-type supercharger |
DE19522551A1 (de) * | 1995-06-21 | 1997-01-02 | Sihi Ind Consult Gmbh | Zweiwellen-Verdrängermaschine |
DE19522557A1 (de) * | 1995-06-21 | 1997-01-02 | Sihi Ind Consult Gmbh | Drehkolbenverdichter, insbesondere Vakuumpumpe |
US6129534A (en) * | 1999-06-16 | 2000-10-10 | The Boc Group Plc | Vacuum pumps |
DE102005017575A1 (de) * | 2004-08-05 | 2006-03-16 | Börger GmbH | Drehkolbenpumpe mit einem Pumpengehäuse und zwei zweiflügeligen Drehkolben |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103062046A (zh) * | 2013-01-07 | 2013-04-24 | 艾迪机器(杭州)有限公司 | 扭曲式转子泵 |
CN103062046B (zh) * | 2013-01-07 | 2016-01-20 | 艾迪机器(杭州)有限公司 | 扭曲式转子泵 |
Also Published As
Publication number | Publication date |
---|---|
EP2042739A1 (fr) | 2009-04-01 |
DE602008000482D1 (de) | 2010-02-11 |
KR20100072289A (ko) | 2010-06-30 |
CN101809290A (zh) | 2010-08-18 |
ATE453801T1 (de) | 2010-01-15 |
EP2042739B1 (fr) | 2009-12-30 |
JP2010540824A (ja) | 2010-12-24 |
FR2921444A1 (fr) | 2009-03-27 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2042739B1 (fr) | Pompe à vide à deux rotors hélicoïdaux | |
BE1014892A5 (fr) | Compresseur a vis sans huile. | |
EP2798223B1 (fr) | Adaptateur pour pompes à vide et dispositif de pompage associé | |
FR2559847A1 (fr) | Machine a volutes pour comprimer un fluide | |
FR2845434A1 (fr) | Compresseur a dioxyde de carbone hermetique a deux etages | |
EP3607204B1 (fr) | Groupe de pompage et utilisation | |
EP3921515B1 (fr) | Corps de pompe multiétagée et pompe à gaz multiétagée | |
FR2962772A1 (fr) | Machine a fluide de type roots | |
FR2984425A1 (fr) | Dispositif d'injection d'huile pour compresseur frigorifique a spirales a vitesse variable | |
FR2668551A1 (fr) | Appareil et compresseur a volutes et systeme de refrigeration. | |
FR2947308A1 (fr) | Machine a volutes a etages multiples | |
FR2844843A1 (fr) | Assemblage de compresseur a refoulement | |
WO2021008834A1 (fr) | Groupe de pompage | |
EP2334906B1 (fr) | Machine rotative a losange deformable multifonctions | |
EP1216358B1 (fr) | Compresseur ou pompe a vide a spirales | |
EP3698044A1 (fr) | Pompe a barillet rotatif avec moyens de guidage et de centrage du barillet distincts | |
FR3121716A1 (fr) | Pompe à vide | |
EP1249610A1 (fr) | Atténuateur dynamique du bruit de refoulement sur les machines à vide rotatives | |
FR3117176A1 (fr) | Pompe à vide | |
EP3105455A1 (fr) | Système de pompage et procédé de descente en pression dans un sas de chargement et de déchargement | |
FR3118650A1 (fr) | Etage de pompage et pompe à vide sèche | |
WO2024088630A1 (fr) | Groupe de pompage | |
FR3128747A1 (fr) | Pompe à vide multi-étagée | |
FR3112176A1 (fr) | Pompe à vide primaire et Installation | |
WO2001073266A1 (fr) | Machine motrice et receptrice a mouvement rotatif |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 200880109072.2 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 08804782 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2010526301 Country of ref document: JP |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
ENP | Entry into the national phase |
Ref document number: 20107008932 Country of ref document: KR Kind code of ref document: A |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 08804782 Country of ref document: EP Kind code of ref document: A1 |