EP3104014A1 - Étage de pompe à vide à canal latéral avec une section transversale de canal présentant une courbure particulière - Google Patents

Étage de pompe à vide à canal latéral avec une section transversale de canal présentant une courbure particulière Download PDF

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Publication number
EP3104014A1
EP3104014A1 EP16171240.1A EP16171240A EP3104014A1 EP 3104014 A1 EP3104014 A1 EP 3104014A1 EP 16171240 A EP16171240 A EP 16171240A EP 3104014 A1 EP3104014 A1 EP 3104014A1
Authority
EP
European Patent Office
Prior art keywords
rotor
channel
side channel
blade
blades
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
EP16171240.1A
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German (de)
English (en)
Other versions
EP3104014B1 (fr
Inventor
Sebastian Oberbeck
Aleksandr Shirinov
Michael Schweighöfer
Tobias Stoll
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.)
Pfeiffer Vacuum GmbH
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Pfeiffer 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
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Publication of EP3104014A1 publication Critical patent/EP3104014A1/fr
Application granted granted Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • F04D17/168—Pumps specially adapted to produce a vacuum
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/008—Regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/403—Casings; Connections of working fluid especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/50—Intrinsic material properties or characteristics
    • F05D2300/516—Surface roughness

Definitions

  • the invention relates to a vacuum pumping stage.
  • the prior art includes vacuum pumping stages of screw pumps, which essentially consist of two parts, namely a stator and a rotor rotating in the stator. Multi-start threads are mounted on the outer diameter of the rotor and on the inner diameter of the stator.
  • Side channel pumps that is to say pumps which have at least one vacuum pump stage in the form of a side channel pumping stage
  • pumps which have at least one vacuum pump stage in the form of a side channel pumping stage
  • These can for example be combined well with turbomolecular pumps or other molecular pumps.
  • the rotor parts of both pumps can be accommodated on a shaft, so that both form a structural unit.
  • the side channel pumping stages usually have an impeller, that is to say a rotor, which has peripheral blades in a channel at its edge.
  • a further embodiment relates to a vacuum pumping stage having an inlet, an outlet and a channel, which has two side walls and a channel bottom, wherein a rotor with a rotor portion dips into the channel and by pumping action of rotor portion and channel is achieved, and with an intermediate Inlet and outlet arranged breaker.
  • Vacuum pumps or vacuum pump assemblies composed of vacuum pumps are used to generate such vacuum conditions.
  • vacuum pump stages are used according to different principles of action, which are adapted to different pressure ranges to compress gas from the desired final vacuum to the atmosphere.
  • side channel pumping stages are used to compress the atmosphere.
  • these blades run around in a channel and promote a vortex-like gas flow between inlet and outlet.
  • the gas stream follows the blades during the circulation and is at a so-called scraper or breaker detached and supplied to the outlet.
  • Such side channel pumping stages are for example in the DE 10 2009 021 642 A1 and the DE 10 2010 019 940 A1 disclosed.
  • the prior art ( DE 33 17 868 A1 ) includes a friction pump in which surface areas with different roughness are present at least in a part of the pump-active surfaces, such that the roughness of the area facing away from the conveying direction surface areas is greater than the roughness of the surface areas facing the conveying direction.
  • This prior art friction pump can be further improved in terms of pumping action.
  • JP H 01 267390 A a side channel pump, in which a plurality of side channels are arranged, which are designed to interact with pump-active surfaces of the rotor.
  • the prior art vacuum pump can be further improved in terms of pumping power.
  • the invention further relates to a further vacuum pumping stage in which a breaker is arranged between the inlet and the outlet.
  • the prior art ( DE 103 34 950 A1 ) includes a side channel compressor having an inlet, an outlet and a rotor and a channel, wherein the rotor is immersed with a rotor portion in the channel and a pumping action is achieved by cooperation of rotor portion and channel.
  • the rotor usually dips into the channel with rotor blades arranged on the rotor.
  • a breaker is arranged between the inlet and the outlet.
  • the breaker encloses the rotor on all sides and, as is known in practice, abruptly in the vicinity of the rotor Outlet where the side channel ends, as well as near the inlet where the side channel begins.
  • the breaker is designed such that the rotor blades uniformly increasingly enclosed, or released evenly decreasing again.
  • the respective rotor blade is thus gradually enclosed by the breaker and constantly, or again continuously released. It does not come to an abrupt, but a continuous and uniform stripping of the compressed gas components of the respective rotor blades.
  • This measure is implemented at the beginning as well as at the end of the breaker, ie at the inlet and at the outlet. As a result, the formation of disturbing sound components in the interrupter area is suppressed and a gas flow at the discharge nozzle is reduced. This leads to an increase in the efficiency.
  • This belonging to the prior art embodiment has the disadvantage that the efficiency is not fully exploited.
  • the technical problem underlying the invention is to provide an improved vacuum pumping stage for threaded or side channel pumps, which are used in molecular and viscous pressure ranges to achieve an increase in performance of the pump.
  • the object of the invention is achieved by a vacuum pumping stage with the features of claim 1.
  • This vacuum pumping stage according to the invention has the advantage that the side channel has a significant improvement in the vacuum technical data of side channel pumps compared to a rectangular side channel, as it belongs to the prior art. At the same time, the side channel according to the invention is easy to manufacture.
  • the curvature of the side walls is concave. This training achieves the best vacuum technical values.
  • the channel is formed axially symmetrical to a median plane of the rotor.
  • the curvature of the at least one side wall in cross section is in each case semicircular.
  • the rotor blades of the rotors are formed in cross-section V-shaped. This shape of the rotor blades has yielded the best pumping power with the curved side walls of the channel.
  • the rotor blades on a blade bottom on a supernatant are designed such that a projection is provided over a blade root of the rotor blades. This means that the material of the rotor blades is not worn down to the bottom of the blade, but that a supernatant is present. This supernatant also has an advantageous effect on the pumping power of the vacuum pumping stage.
  • the projection above the blade root to the rotor blade center is tapered.
  • the projection above the blade root to the rotor blade center is seen in the axial direction is tapered. This means that at the axial edges of the blades, the blades are worn down to the blade base and that the supernatant over the blade base is maximally formed toward the center.
  • a further advantageous embodiment provides that the rotor blades are arranged completely in their height in the side channel. This also achieves optimized pump performance.
  • the blade root of the rotor blades and a radially arranged in the direction of the shaft boundary surface of the side channel are arranged in the radial direction at the same height. This means that the rotor blades are completely arranged in the side channel and unfold their full effect there.
  • the boundary surface arranged radially in the direction of the shaft is the surface of the side channel, which is arranged opposite the channel bottom.
  • a blade root radius and a radius of the boundary surface of the side channel arranged radially in the direction of the shaft have the same size R S 1 .
  • a blade root radius and a radius of the radially arranged in the direction of the shaft boundary surface of the side channel on the same size R S 1 also significantly increases the pumping effect.
  • an axial gap ( ⁇ ) is provided between the rotor and stator disks, and the axial gap is configured as follows: ⁇ ⁇ 0 . 3 mm f u ⁇ r p 2 ⁇ 10 mbar ⁇ ⁇ 0 . 2 mm f u ⁇ r 10 mbar ⁇ p 2 ⁇ 100 mbar ⁇ ⁇ 0 . 15 mm f u ⁇ r p 2 > 100 mbar ,
  • a further advantageous embodiment of the vacuum pump stage provides that with increasing speed and increasing peripheral speed of the rotor disks of the side channel radius R S 3 and the distance d S 1 , is increasingly formed. This also has a positive influence on the pumping power.
  • a blade height of the rotor blades is 60% to 100% of a rotor disk width. This serves to further improve the pump power.
  • the optimum blade height is advantageously 60% to 100% of the rotor disk width.
  • the optimum side channel radius depends on the peripheral speed of the rotor disc.
  • the side channel radius is advantageously formed between 80% to 120% of the rotor disk width.
  • a width d S 1 of the channel arc is preferably between 20% and 120% of the rotor disc width.
  • a blade spacing of the rotor blades is advantageously between 50% and 100% of the rotor disk width.
  • the blade clearance is less than or equal to 55% of the rotor disk width with a side channel area which is smaller than 2.5 times the blade area.
  • a blade spacing of 50% of the rotor disk width is particularly advantageous for side channels with a side channel area no greater than 2.5 times the blade area. These are small side channels.
  • the blade spacing is greater than or equal to 85% of the rotor disk width with a side channel area that is greater than 5 times the blade area. These are big side channels.
  • the optimum number of blades thus becomes smaller with increasing side channels, or the optimum distance between the blades is larger.
  • the minimum web width is formed depending on the manufacturing accuracy and the material strength of the rotor disk. This ensures the stability of the rotor disk.
  • Fig. 1 shows a vacuum pump with a housing 1 and three pumping units 14, 16, 18.
  • the housing 1 is provided with a gas inlet opening 2 and a gas outlet opening 4.
  • the pump units consist of rotating and fixed gas-conveying components.
  • the rotating components are mounted on a shaft 6 in the axial direction one behind the other.
  • To operate the shaft 6 includes a drive system 8 and bearing elements 10 and 12.
  • the fixed components are firmly connected to the housing 1.
  • One of the gas inlet opening facing pump unit 14 is formed as a turbomolecular pump.
  • the following in the direction of gas flow pump unit 16 consists of several subunits 16a, 16b, 16c. These each have one or more molecular pumping stages according to the type of Gaede, hereinafter called Gaede stages. Within the subunits, the Gaede stages are connected in parallel. The subunits themselves are connected in series. This means that connecting elements 34a for the subunit 16a and 34b for the subunit 16b, the input sides and on the other side, the output sides of Gaede stages together so that a parallel gas flow in the individual subunits is made possible.
  • the subunits are interconnected by connecting members 36a, 36b and 36c so that the output side of one subunit is connected to the input side of the following subunit, respectively.
  • the gas outlet opening facing pump unit 18 is a multi-stage side channel pump educated. In the Fig. 1 shown pump is shown only by way of example.
  • the invention relates to all vacuum pumps in which side channel pumping stages and / or screw pumps are provided.
  • grooves are arranged in the surface of thread grooves and / or that grooves are arranged in the surfaces of stators and / or rotors.
  • the Fig. 2 to 6 show possible structures that are uniformly mounted in a surface 41, such as a thread groove of a side channel or on a rotor.
  • Fig. 2 shows a structure with grooves 40 having a rounded bottom.
  • the grooves 40 are arcuate.
  • Fig. 3 shows a trapezoidal structure with a conically tapering cross section
  • Fig. 4 shows a triangular structure with a conically tapering cross section.
  • Fig. 5 is shown a rectangular structure.
  • Fig. 6 again shows a triangular structure having an asymmetric configuration.
  • the depth of the grooves 40 may vary from 1 ⁇ m to 100 ⁇ m.
  • the groove width, or the distance between the individual grooves 40, can vary from 1 ⁇ m to 1 mm.
  • the grooves 40 may be along the flow direction, transverse to the flow direction and at an angle to the Flow direction of the gas are incorporated into the surface 41.
  • the grooves 40 can also be generated with a grindstone in a surface 41.
  • the grooves 40 have an irregular structure in this case.
  • the rough surface should have a roughness of 0.1 .mu.m to 100 .mu.m, preferably from 2 .mu.m to 100 .mu.m.
  • all profiles in the Fig. 2 to 7 are shown formed in the grooves 40 standing air, so that the gas friction on the surface 41 is reduced. This effect affects the sliding of gas layers. By influencing these so-called boundary layer forces, a sliding of the gases on the surface of the pump-active surfaces is favored. As a result, the speed of the circulation flow and the intensity of the energy exchange between the pump-active surfaces of the rotor and stator is increased. This leads to an increase in compression, a reduction in power consumption and an increase in pumping speed.
  • Fig. 8 is a thread groove 50 of a threaded pump shown.
  • the thread groove 50 which is arranged, for example, in a stator 51, as well as the adjoining surfaces of the thread groove 50 are coated with a coating 52 which reduces the friction and improves the sliding properties of the surface compared to an uncoated surface, for example a metal surface, for example aluminum or stainless steel. Also by this measure, the gas friction is reduced at the channel surface, whereby the above advantages occur.
  • Fig. 9 shows a vacuum pump 100 with a gas inlet 102 and a gas outlet 103 and a housing 101.
  • the housing 101 is composed of four housing parts 120, 121, 122, 123 constructed, which accommodate the components of the vacuum pump 100.
  • Gas entering the vacuum pump 100 through the gas inlet 102 first enters a molecular stage 105. It has an inner stator 505 provided with an internal thread groove 507 and an outer stator 506 provided with an outer thread groove 508. Between inner stator and outer stator, a smooth surface cylinder 502 is provided, which is connected to the rotor 500.
  • the molecular step 105 is thus designed as a Holweck stage. In the Fig. 9 Holweck stage shown is symmetrical with a surrounding of stator components second cylinder 502 'and therefore operates in two stages.
  • the rotor is connected to a shaft 108, which is rotatably mounted in rolling bearings 110 and 111.
  • rolling bearings 110, 111 passive and active magnetic bearings can also be used.
  • On the shaft 108 at least one permanent magnet 113 is arranged, which cooperates with a stationary coil 112 and forms a drive 107 together with this.
  • the rolling bearing 110, the drive 107 and the molecular stage 105 are arranged in the housing parts 120, 121.
  • the shaft 108 passes through the housing part 122, which includes a side channel pumping stage 104.
  • the side channel pumping stage 104 is formed by a side channel 401 and an impeller 400, wherein on the impeller 400 at least one blade 402 is arranged, which rotates in the side channel by the rotation of the shaft 108 and thus generates the pumping action.
  • Gas passes through a transfer channel 124 from the molecular stage 105 into the side channel stage 104 and is expelled through another transfer channel 125.
  • the gas passes through the transfer channel 125 in a Vorvakuumform 106.
  • This is also designed as a Sokanalpumpcut, in which case the geometry of the arranged on the impeller 600 and rotating in the side channel 601 blades 602 of the geometry of the blades 402. From this pumping stage 106, the gas from the vacuum pump 100 is discharged through the gas outlet 103.
  • Fig. 10 shows a section through the housing part 122 along the line II of Fig. 9 ,
  • the impeller 400 sits on the shaft 108.
  • This has an edge 403, on which along the circumference evenly distributed blades 402 are arranged.
  • the side channel 401 surrounds the impeller, wherein the side channel in the radial direction surrounds the blade region of the impeller in a substantially annular manner. Only over part of the circumference of the housing adjacent to the impeller.
  • This section forms a breaker 404 which separates the suction and discharge sides and at which the gas flow, which forms in the side channel and follows the rotation of the impeller, is detached therefrom and transferred to the transfer channel 125.
  • the side channel 401 has a channel bottom 420 and two side walls 421, 422.
  • the side walls 421, 422 are curved. That is, they have a concave shape.
  • the vanes 402 of the impeller or rotor 400 fully protrude into the side channel 401.
  • a radius R S 1 of a blade root 423 is the same size as the radius R S 1 of a radially arranged in the direction of the shaft boundary surface 424 of the side channel 401st
  • the vanes 402 are completely immersed in the side channel 401.
  • the pumping power of the side channel pumping stage is significantly improved.
  • the web between the blades as low as possible (not shown).
  • the volume of gas filled with gas should be as large as possible.
  • Improvements in vacuum technology data are also achieved by optimizing the side channel radius R S 3 (80% to 120% of the rotor width) and the distance between two centers of the side channel semicircles d S 1 (20% to 120% of the rotor width).
  • the optimum radius R S 3 and distance d S 1 depend on the peripheral speed of the rotor disk and on the blade size.
  • the dimensions R R 1 , R R 3 , d R 1 , blade height h and blade angle ⁇ are predetermined.
  • the dimension R S 1 is predetermined by the lower blade edge of the rotor disk.
  • ⁇ denotes the axial gap between the rotor and the stator disc.
  • the axial gap ⁇ may preferably be from 0.01 mm to 0.5 mm. Small axial gaps are useful on the discharge side and large axial gaps on the suction side. If a labyrinth seal is used on the axial surface between the rotor and the stator disks, the axial gap may be more than 0.5 mm.
  • the guideline values for the axial gaps can be selected as follows: ⁇ ⁇ 0 . 3 mm f u ⁇ r p 2 ⁇ 10 mbar ⁇ ⁇ 0 . 2 mm f u ⁇ r 10 mbar ⁇ p 2 ⁇ 100 mbar ⁇ ⁇ 0 . 15 mm f u ⁇ r p 2 > 100 mbar
  • Fig. 12 a comparison of rectangular in cross-sectional side channels and side channels with two semi-circular in cross-section side walls with V-shaped rotor blades at 800 Hz and 1000 Hz rotational frequency in comparison is shown.
  • the curves 716, 717, 718, 719 represent the course of the compression as a function of the pressure.
  • the lower two curves 718, 719 refer to a rotation frequency of 800 Hz.
  • a side channel with semicircular side walls has a higher compression (curve 718). on as a prior art belonging in the cross section rectangular channel (curve 719).
  • the two upper curves 716, 717 refer to a rotational frequency of 1000 Hz.
  • the upper curve 716 represents the compression as a function of pressure for a side channel with semi-circular semicircular side walls. Again, this is the Compression by the inventive design of the side channel significantly increased compared to a side channel with a rectangular cross-section (curve 717). It can be seen that the side channels with two semi-circular in cross-section side walls have a much better compression.
  • Fig. 13 the dependence of the compression factor on the axial gap is shown. Like the legend in Fig. 13 As can be seen above, axial gaps between 0.15 mm and 0.4 mm have been detected. The compression factor k 0 is greater, the smaller the axial gap is.
  • rotor disks of a multi-stage side channel pump with the same blade size have the same speed, but depending on the rotor disc diameter R R 1 have different peripheral speeds. For this reason, rotor disks with different diameters R R 1 and the same blade size should have side channels with different radii R S3 and distances d S 1 .
  • Fig. 16 shows the impeller 400 with the blades 402.
  • the blades 402 are V-shaped.
  • the blade ground has in the region of a median plane 425 of the impeller 400 a projection that rises from edges 426, 427 of the blade root to the median plane 425.
  • the impeller 400 rotates in the direction of arrow A.
  • Fig. 17 shows the impeller 400 according to Fig. 16 in side view in the direction of arrow B.
  • the impeller 400 carries the V-shaped blades 402.
  • the blades have a blade base 423 on. Above the blade bottom 423 is a projection 428 over.
  • An optimal blade height is 60% to 100% of the rotor disk width.
  • An optimum side channel radius depends on the peripheral speed of the rotor disk 400 and may be from 80% to 120% of the rotor disk width.
  • the distance d S 1 also depends on the peripheral speed of the rotor disk and can be from 20% to 120% of the rotor disk width.
  • the optimum number of blades or the optimal distance between the blades does not depend on the speed.
  • the optimal distance between the blades is proportional to the blade size and also depends on the side channel size. It is from 5o% to 100% of the rotor disk width, the optimum spacing between the blades is less than or equal to 55% for small side channels (side channel area no greater than 2.5 times the blade area) and greater than or equal to 85% for large side channels (side channel area not less than 5 times the blade area).
  • the optimum number of blades thus becomes smaller with increasing side channels, or the optimum distance between blades is larger.
  • the side channel area A SK and the blade area A Sch can be calculated using equations 4 to 7.
  • the web width of the blades should be as small as possible.
  • the minimum web width is limited by the manufacturing accuracy and the material strength of the rotor disk.
  • Fig. 18 to 20 show further design possibilities of a side channel.
  • the side channel 401 is circular in shape.
  • the side channel 401 has no plan side channel bottom, but overall a circular cross-section.
  • the side channel 401 is also circular. However, the radius of the side channel 401 is smaller than in FIG Fig. 18 shown.
  • the side channel 401 has concave side walls 421, 422.
  • the channel bottom 420 is flat.
  • the side channel cross-sectional diameter is advantageously formed constant over the entire circumference of the side channel.
  • the side channel cross section diameter decreases from an inlet 124 to an outlet 125.
  • the inlet 124 and the outlet 125 are diametrically opposed.
  • an inlet 124 ' is drawn.
  • the side channel cross-sectional diameter can decrease from the inlet 124 'to the outlet 125. This reduction can be linear with the circumferential angle. It can also be another function of the circumferential angle.
  • a side channel surface is shown with a centerline 126 of the side channel as a function of radius and angle ⁇ .
  • the reduction of the side channel area may, as in Fig. 21a shown, done from above. It can also be done from below, as in the illustration Fig. 21b shown. However, it can also be done from above and from below, as in the illustration Fig. 21c shown.
  • the side channel diameter may also be reduced from one side or both sides along the side channel from the inlet 124 'to the outlet 125. The inlet 124 'is in Fig. 10 shown.
  • Fig. 22 shows a further embodiment of a side channel 401.
  • the side channel 401 has side walls 421, 422 which are formed in a circular section.
  • the channel bottom 420 is also not shown plan in this embodiment, but consists of two circular sections with a radius R S. 3
  • Fig. 23 shows a further embodiment of an embodiment of the side channel 401.
  • the side channel 401 has curved side surfaces 421, 422 and a not plan trained channel bottom 420.
  • the curved side surfaces 421, 422 in this case do not correspond to circular sections.
  • a breaker 404 is in Fig. 10 shown.
  • the breaker is in the side channel pumping stage 104 of Fig. 9 arranged.
  • the description of the figure Fig. 9 and 10 are fully transferable to the present invention.
  • FIG. 12 shows a prior art breaker 404 having an inlet 701 and an outlet 702.
  • the breaker 404 as well as the inlet 701 and the outlet 702 are part of a stator 700.
  • the top view in FIG Fig. 24 shows a side view of the breaker 404.
  • the bottom view shows a plan view of the breaker 404.
  • a rotor 703 is shown in dashed lines in the upper illustration.
  • the rotor 703 rotates at a rotational speed v.
  • the prior art breaker 404 has a region d 1 in which the breaker 404 completely encloses the rotor 703.
  • a side channel 704 ends abruptly. It comes here to disturbing sound components as well as to a gas flow at the discharge nozzle 702.
  • Fig. 25 shows the breaker 404 disposed in the stator 700.
  • an inlet 701 and an outlet 702 are arranged for the side channel 704.
  • a rotor 703 rotates at a speed v.
  • Fig. 25 can be seen in the upper part, the breaker 404 over a length d 1 on a region in which the rotor 703 is completely enclosed by the breaker 404.
  • the breaker In a region over a length d 2 , the breaker has a bevel 705.
  • the side channel 701 widens continuously to its total width outside the range d 2 .
  • Rotor blades 706 are arranged on the rotor 703, only shown schematically.
  • the length d 1 of the breaker is greater than a blade length.
  • the length d 2 of the bevel 705 is longer than a blade length.
  • the channel 701 may have a shape as shown in FIG Fig. 11 for the channel 401 is shown.
  • the rotor 400 is bounded by a sealing surface 707 of the stator. This sealing surface 707 is arranged in the blade-less region of the rotor 400.
  • the chamfer 705 tapers in the direction of the area d 2 of the interrupter 404, in which the interrupter 404 completely surrounds the rotor 703.
  • An angle ⁇ indicates the opening angle of the bevel 705.
  • An angle ⁇ is a complementary angle to the angle ⁇ , that is, the sum of the angles ⁇ and ⁇ together make 180 °.
  • the angle ⁇ corresponds to a blade angle of the rotor blades 706 of the rotor 703, as in FIG Fig. 26 shown.
  • Fig. 26 are a rotor blade 706 in section and the angle of attack ⁇ shown. D denotes the blade height.
  • FIG. 12 illustrates another embodiment of the invention.
  • the breaker 404 formed in the stator 700 has the bevel 705.
  • an additional bevel 706 is provided in the direction of the side channel 704.
  • This additional taper which has a length d 3, an even higher compression and higher pumping speeds can be achieved.
  • Fig. 28 is the compression of a side channel pumping stage shown.
  • the curves show, on the one hand, the values for a standard breaker and, on the other hand, for a breaker form according to FIG Fig. 25 , It can be seen that the compression in accordance with the breaker shape Fig. 25 is increased.
  • Fig. 29 the suction capacity of a side channel pumping stage is shown. It can be seen clearly that the according to Fig. 25 used breaker form leads to a higher suction capacity than a prior art breaker form.
  • Fig. 30 shows the stator 700 with a side channel 704 and an outlet 702.
  • the breaker 404 is adjacent to a surface 708 while maintaining a narrow gap (not shown) on blades of the rotor, which is also not shown here.
  • the breaker has the bevel 705, which widens in the direction of the channel 704.
  • a sealing surface 707 has a lower level than a surface 709 of the stator 700, resulting in the edge or surface 708.
  • the bevel 705 represents on the one hand a radial opening of the interrupter 404 and also an axial recess of the sealing surface 707.
  • the stator 700 has a bore 710 for the passage of a shaft of the rotor (not shown).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Non-Positive Displacement Air Blowers (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP16171240.1A 2013-08-06 2014-07-14 Étage de pompe a vide à canal latéral avec une section transversale de canal présentant une courbure particulière Active EP3104014B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013108482.6A DE102013108482A1 (de) 2013-08-06 2013-08-06 Vakuumpumpstufe
EP14176840.8A EP2835536B1 (fr) 2013-08-06 2014-07-14 Étage de pompe à vide avec rugosité de surface particulière engendrant une réduction du frottement gazeux

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP14176840.8A Division EP2835536B1 (fr) 2013-08-06 2014-07-14 Étage de pompe à vide avec rugosité de surface particulière engendrant une réduction du frottement gazeux
EP14176840.8A Division-Into EP2835536B1 (fr) 2013-08-06 2014-07-14 Étage de pompe à vide avec rugosité de surface particulière engendrant une réduction du frottement gazeux

Publications (2)

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EP16171251.8A Active EP3088743B1 (fr) 2013-08-06 2014-07-14 Étage de pompe a vide à canal latéral avec un barrage de canal qui présente une rampe du côté de l'aspiration
EP16171240.1A Active EP3104014B1 (fr) 2013-08-06 2014-07-14 Étage de pompe a vide à canal latéral avec une section transversale de canal présentant une courbure particulière
EP14176840.8A Active EP2835536B1 (fr) 2013-08-06 2014-07-14 Étage de pompe à vide avec rugosité de surface particulière engendrant une réduction du frottement gazeux

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DE102014109004A1 (de) * 2014-06-26 2015-12-31 Pfeiffer Vacuum Gmbh Siegbahnstufe
DE102017121777A1 (de) * 2017-09-20 2019-03-21 Lutz Pumpen Gmbh Modifizierte Seitenkanalpumpe sowie Verfahren zum Betrieb einer solchen
EP3594498B1 (fr) 2019-11-06 2022-01-05 Pfeiffer Vacuum Gmbh Système avec un dispositif de recyclage des gaz

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JPH01267390A (ja) 1988-04-18 1989-10-25 Daikin Ind Ltd 渦流形真空ポンプ
DE3932288A1 (de) 1989-09-28 1991-04-11 Markus Heinermann Gangschaltungskomponente fuer eine fahrradgangschaltung
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WO2020081422A1 (fr) * 2018-10-15 2020-04-23 The Regents Of The University Of Michigan Optimisation du pompage de viscosités variables par le biais d'une pompe tesla miniaturisée microtexturée
US11519413B2 (en) 2018-10-15 2022-12-06 The Regents Of The University Of Michigan Optimizing pumping of variable viscosities via microtextured miniaturized tesla pump

Also Published As

Publication number Publication date
EP3088743B1 (fr) 2019-12-25
EP2835536A2 (fr) 2015-02-11
EP2835536A3 (fr) 2015-05-06
EP3104014B1 (fr) 2021-09-29
DE102013108482A1 (de) 2015-02-12
EP2835536B1 (fr) 2018-11-28
EP3088743A1 (fr) 2016-11-02

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