EP3325812B1 - Machine à canal latéral (compresseur, pompe à vide, ou ventilateur) avec un conduit de purge dans le barrage - Google Patents

Machine à canal latéral (compresseur, pompe à vide, ou ventilateur) avec un conduit de purge dans le barrage Download PDF

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Publication number
EP3325812B1
EP3325812B1 EP16738825.5A EP16738825A EP3325812B1 EP 3325812 B1 EP3325812 B1 EP 3325812B1 EP 16738825 A EP16738825 A EP 16738825A EP 3325812 B1 EP3325812 B1 EP 3325812B1
Authority
EP
European Patent Office
Prior art keywords
gas
channel
side channel
gas outlet
impeller
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.)
Active
Application number
EP16738825.5A
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German (de)
English (en)
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EP3325812A1 (fr
Inventor
Rudi Dittmar
Peter Fischer
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.)
Gardner Denver Deutschland GmbH
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Gardner Denver Deutschland GmbH
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Filing date
Publication date
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Priority to EP20205155.3A priority Critical patent/EP3792495A1/fr
Publication of EP3325812A1 publication Critical patent/EP3325812A1/fr
Application granted granted Critical
Publication of EP3325812B1 publication Critical patent/EP3325812B1/fr
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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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/009—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by bleeding, by passing or recycling fluid
    • 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides 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
    • F04D29/18—Rotors
    • F04D29/188—Rotors specially for 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps 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
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing 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
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F04D5/007—Details of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F04D5/008—Details of the stator, e.g. channel shape

Definitions

  • the invention relates to a side channel machine according to the preamble of claim 1.
  • Side channel machines are generally known from the prior art. Side channel machines are able to convey or compress gas. From the DE 197 08 953 A1 side channel blowers according to the preamble of claim 1 are known. According to one embodiment, an interrupter is provided with at least one outlet channel which diverts at least part of a volume flow flowing over the interrupter and opens into the gas inlet of the side channel compressor. The efficiency of this side channel compressor is not satisfactory.
  • EP 0 011 983 A1 EP 0 636 792 A1 and DE 24 09 183 A1 other side channel machines are known.
  • Generic side channel machines are also from the DE 103 34 950 A1 , DE 103 34 812 A1 or. DE 199 06 515 C1 for example known.
  • the invention is based on the object of providing a side channel machine which has a particularly high degree of efficiency and operates extremely quietly. Furthermore, the side channel machine should have a very high power density.
  • Geometry optimization and targeted flow guidance of the side channel machine bring about an improvement of at least one performance parameter of the same.
  • the power density, the efficiency and / or the noise development of the side-channel machine is improved compared to conventional side-channel machines.
  • the gas to be conveyed is preferably air or a technical gas.
  • the side channel machine is preferably designed as a side channel blower or side channel compressor. It is advantageous if the side channel machine is able to work in vacuum and / or compressor mode.
  • An interrupter gas mass flow can be safely discharged into the at least one gas outlet connector through the at least one discharge channel.
  • the at least one discharge channel is advantageously circular in cross section and preferably runs radially with respect to the axis of rotation. In particular, it extends straight.
  • the gas can be sucked in a functionally reliable manner from at least one of the impeller cells adjacent to the at least one discharge channel. It is advantageous if the cross-sectional constriction necessary to form the Venturi arrangement is present in the at least one gas outlet nozzle.
  • the side channel machine is designed in one or more stages.
  • the at least one gas inlet opening and the at least one gas outlet opening are in the flow direction of the gas about the axis of rotation arranged at a distance from one another. It is advantageous if there is an angle about the axis of rotation of at least 170 ° between them.
  • the impeller is favorably in direct or indirect drive connection with a motor or drive.
  • the at least one interrupter is preferably mounted on the housing or is an integral part of the same.
  • the at least one gas inlet nozzle and / or the at least one gas outlet nozzle is / are preferably mounted on the housing or an integral part of the same.
  • the gas is conveyed from the at least one gas inlet opening in a flow direction around the axis of rotation to the at least one gas outlet opening, which is arranged downstream of the at least one gas inlet opening.
  • the gas is thus guided in the side channel in a substantially ring-like manner. It is preferably pressed radially outward in the side channel by the centrifugal force and then guided back to the radially inner area of the side channel in relation to the axis of rotation, where it re-enters impeller cells between adjacent impeller blades and is again subject to centrifugal force.
  • the side channel machine has two impeller flows.
  • a gas inlet connection is assigned to each impeller inlet.
  • the at least one gas outlet connector is connected essentially tangentially to the side channel for the essentially tangential removal of the gas from the side channel.
  • the essentially tangential arrangement of the at least one gas outlet connection on the side channel means that pressure losses can be reduced, which leads to an improvement in the efficiency of the side channel machine. It is advantageous if the at least one gas outlet connection is connected absolutely tangentially to the side channel for the tangential removal of the gas from the side channel.
  • the at least one Gas outlet connection is essentially seamless and essentially tangential to the ceiling.
  • vortex shedding on the impeller blades and on the at least one gas outlet nozzle can be reduced, so that characteristic curve losses or pressure losses can be avoided.
  • operating noises of the side channel machine can be reduced in this way.
  • the at least one gas outlet connector connects absolutely seamlessly and tangentially to a cover that delimits the side channel radially outward.
  • the side channel is preferably delimited by a base that is radially inner in relation to the axis of rotation, the at least one gas outlet connecting to the base in a substantially seamless manner and substantially tangentially. It is advantageous if the at least one gas outlet connection connects absolutely seamlessly and tangentially to a base which delimits the side channel radially inward.
  • a flow cross-section in the at least one gas outlet nozzle widens at least in some areas in the flow direction of the gas, preferably at least in an upstream starting area of the at least one gas outlet nozzle opposing flow guide walls of the at least one gas outlet nozzle having an angle of expansion of at most 11 °, more preferably not more than 9 °, to each other.
  • the at least one gas outlet connector has at least one wall, preferably radially inner with respect to the axis of rotation, which wall is essentially parallel to an absolute velocity vector of the gas flowing in the side channel adjacent downstream to the at least one interrupter.
  • the gas thus favorably brushes along the at least one wall of the at least one gas outlet connection.
  • there is at least one wall on the at least one interrupter It is expedient if the at least one wall runs absolutely parallel to an absolute velocity vector of the gas flowing in the side channel adjacent upstream of the at least one interrupter.
  • dependent claim 2 prevents gas from inadvertently flowing back from the at least one gas outlet into the side channel or the at least one interrupter at certain operating points of the side channel machine, which would be unfavorable in terms of efficiency and noise development. It is advantageous if the at least one valve is arranged essentially on the outlet side with respect to the flow of the gas on the at least one interrupter.
  • the gas can be sucked in a functionally reliable manner from at least one of the impeller cells adjacent to the at least one discharge channel.
  • the side channel machine has at least one suction channel adjoining a discharge channel for sucking the gas enclosed in at least one of the impeller cells adjacent to the at least one discharge channel from the Side channel in the side channel at a distance from the at least one discharge channel having.
  • the gas can be sucked in a functionally reliable manner from at least one of the impeller cells adjacent to the at least one discharge channel.
  • a total cross-sectional area of the at least one suction channel is advantageously between 0.001 x total volume of the impeller cells of the impeller and 0.006 x total volume of the impeller cells of the impeller.
  • At least one relief groove starting from the side channel is arranged in the at least one interrupter.
  • the at least one expansion groove can reduce the expansion noise of the gas that arises during the operation of the side channel machine due to the tensioned interrupter gas mass flow emerging from the impeller cells.
  • useful volume flows can be reduced by blocking an inflow cross section.
  • a minimum distance of 1.1 to 2 times is preferably between an upstream start of the at least one expansion groove and an impeller cell opening of at least one of the impeller cells adjacent to the at least one expansion groove in the circumferential direction around the longitudinal central axis , 0 times, more preferably from 1.4 times to 1.6 times, the distance between adjacent impeller blades from one another in the circumferential direction around the axis of rotation.
  • the at least one relaxation groove is shaped in such a way that the gas is able to sweep along the wall of the interrupter that delimits the at least one relaxation groove, at least in regions. This configuration effectively prevents the generation of noise and turbulence.
  • a conventional side channel blower 1 comprises an impeller 3 provided with impeller blades 2, which is rotatably mounted in a housing 4 about a longitudinal center axis or axis of rotation 5.
  • a conventional drive 7 is used to drive the impeller 3 in rotation. The gas is accordingly conveyed in the housing 4.
  • the housing 4 comprises a first housing part 8 and a second housing part 9.
  • the first housing part 8 and the second housing part 9 are shown in FIG Fig. 1 assembled and together enclose the rotatably drivable impeller 3 with the impeller blades 2, which is arranged on a drive shaft 10 in a rotationally fixed manner.
  • the impeller 3 is designed like a disk. It comprises an inner impeller hub 11 with a central, circular hub bore 12.
  • the impeller hub 11 is formed by an inner hub base 13 that delimits the hub bore 12 radially outward and a radial, annular hub disk 14 that adjoins this.
  • the impeller 3 comprises a radially outer support ring 15 which is attached to the outside Hub disk 14 adjoins and this overlaps on both sides in the direction of the longitudinal center axis 5.
  • the support ring 15 carries a multiplicity of impeller blades 2 distributed in the circumferential direction, which protrude radially from the support ring 15.
  • the impeller blades 2 are arranged equidistant from one another.
  • the impeller blades 2 limit the impeller cells 50 in the circumferential direction.
  • the central hub bore 12 is used to accommodate the drive shaft 10.
  • a conventional feather key connection is provided between the drive shaft 10 and the hub base 13 to transmit a torque applied by the drive shaft 10 to the impeller hub 11 to rotate the impeller 3.
  • the first housing part 8 has a central hub section 16 which delimits a partial hub receiving space 17 radially and axially.
  • the hub section 16 is penetrated by a central shaft bore 18 which opens into the partial hub receiving space 17.
  • the hub section 16 is followed by an annular side wall 19 which extends radially outward from the hub section 16.
  • a circumferential channel section 20 adjoins the side wall 19 on the outside.
  • the hub section 16, the side wall 19 and the channel section 20 are designed as a one-piece cast part and form the first housing part 8.
  • the hub section 22 is followed by an annular side wall 24 which extends radially outward.
  • a circumferential channel section 25 is connected on the outside with the side wall 24.
  • a roller bearing 26 for the drive shaft 10 is arranged in the hub section 22.
  • the hub section 22, the side wall 24 and the channel section 25 are designed as a one-piece cast part and together form the second housing part 9.
  • the first housing part 8 and the second housing part 9 are connected to one another in the assembled state in such a way that the two partial hub receiving spaces 17, 23 together delimit a hub receiving space 27 and the two channel sections 20, 25 together define a side channel 28 limit for conveying the gas.
  • the two side walls 19, 24 run parallel to one another at a distance.
  • the side channel 28 extends in a ring around the longitudinal center axis 5.
  • the second housing part 9 is advantageously designed as a housing cover which can be removed from the first housing part 8.
  • a reverse configuration is alternatively possible.
  • the side channel blower 1 has two gas inlet connections 29.
  • a gas inlet connection 29 is arranged on each housing part 8, 9.
  • Each gas inlet connector 29 supplies a flood of the side channel 28.
  • the gas to be conveyed can be introduced into the side channel fan 1 in a flow direction 30 via the gas inlet connector 29 when the side channel blower 1 is in operation.
  • the side channel blower 1 also has a gas outlet connection (not shown), which is formed by the two housing parts 8, 9.
  • the gas outlet connection is in flow connection with the side channel 28.
  • the gas can be discharged from the side channel blower 1 in a flow direction 32 via the gas outlet connection.
  • the gas inlet nozzle 29 and the gas outlet nozzle extend essentially perpendicular to one another.
  • the side channel blower 1 In the hub receiving space 27 delimited by the hub sections 16, 22, the side channel blower 1 is in the assembled state the hub foot 13 of the impeller 3 is arranged, the hub bore 12 being penetrated by the drive shaft 10. Between the spaced-apart side walls 18, 24 of the housing 4, the hub disk 14 of the impeller 3 extends radially outward from the hub base 13. The support ring 15 and the impeller blades 2 are located in the circumferential side channel 28.
  • FIG Fig. 2 a first embodiment described, which is like the following embodiments in the side channel blower 1 according to FIG Fig. 1 Can apply.
  • Identical components are given the same reference numerals as in the side channel blower 1 according to FIG Fig. 1 .
  • Functionally identical, but structurally different components are given the same reference numerals with a subordinate "a”.
  • the side channel 28 is spatially delimited radially inward by a floor 35 and radially outward by a ceiling 36 in relation to the longitudinal center axis 5.
  • the floor 35 and the ceiling 36 lie opposite one another and run at a distance from one another, delimiting the side channel 28. They are formed on the housing 4a.
  • a gas outlet nozzle 31a is connected essentially tangentially to the side channel 28, so that gas conveyed in a conveying direction 6 leaves the side channel 28 via a gas outlet opening 33 in the housing 4a essentially tangentially.
  • a gas deflection point at which the conveyed gas is slightly radially outward with respect to the Longitudinal central axis 5 is deflected.
  • the conveyed gas is slightly deflected both in the area of the floor 35 and in the area of the ceiling 36.
  • the gas outlet connector 31a widens substantially uniformly in the flow direction 32 of the gas.
  • the at least one gas inlet connector 29a is connected essentially tangentially to the side channel 28, so that the conveyed gas enters the side channel 28 essentially tangentially via at least one gas inlet opening 34 in the housing 4a.
  • the essentially tangential arrangement of the nozzles 29a, 31a on the side channel 28 means that pressure losses in the side channel blower 1a can be effectively reduced.
  • a switch 39 is arranged in the side channel 28 between the gas outlet opening 33 and the at least one gas inlet opening 34.
  • the interrupter 39 has a side wall 40 adjacent to the gas outlet opening 33. Furthermore, the interrupter 39 has an inner wall 41 which is radially inner in relation to the longitudinal center axis 5 and a radially outer outer wall 42 opposite the inner wall 41.
  • FIG Fig. 3 a second embodiment described. Structurally identical components are given the same reference numerals as in the side channel blowers 1, 1a according to FIG Fig. 1 or 2. Functionally similar, but structurally different components are given the same reference numerals with a subsequent "b".
  • the at least one gas inlet connector 29a is again connected to the side channel 28 essentially tangentially.
  • the gas outlet connector 31b connects absolutely or completely tangentially to the side channel 28. According to Fig. 3 the connection between the side channel 28 and the gas outlet nozzle 31b is seamless. This applies to both the radially inner and the radially outer guidance of the gas in relation to the longitudinal center axis 5.
  • the gas outlet connection 31b widens downstream to the gas outlet opening 33.
  • an inner flow guide wall 37 of the gas outlet connector 31b, which adjoins the base 35, deviates by an angle b from a parallel to an opposite outer flow guide wall 38 of the gas outlet connector 31b, as in FIG Fig. 3 is shown in dashed lines.
  • the angle b is a maximum of 9 °.
  • connection angle c is advantageously a connection angle c about the longitudinal center axis 5, which is between 290 ° and 310 °.
  • the interrupter 39c is penetrated by a discharge channel 43 which extends between the inner wall 41 of the interrupter 39c and the outer wall 42 of the interrupter 39c radially with respect to the longitudinal center axis 5.
  • the discharge channel 43 has a cross-sectional area A.
  • a suction channel 44 adjoins the discharge channel 43 on the downstream side, radially on the inside, and opens into the side channel 28 at a distance from the discharge channel 43.
  • the mouth or inlet opening 45 of the suction channel 44 into the side channel 28 is located approximately opposite the discharge channel 43.
  • the inlet opening 45 is spaced from the discharge channel 43 by an angle d about the longitudinal center axis 5, which is between 120 ° and 140 °.
  • the suction channel 44 has a larger, in particular significantly larger, cross-sectional area B than the discharge channel 43.
  • gas is sucked out of an impeller cell 50 of the rotating impeller 3, which is located just adjacent to an inlet opening 56 of the discharge channel 43 opening into the side channel 28.
  • the gas transport can be achieved, for example, through corresponding pressure differences, in particular between inlet opening 56 and inlet opening 45. In particular, the pressure prevailing at the inlet opening 45 is lower than at the inlet opening 56.
  • the impeller cells 50 are spatially delimited in the circumferential direction of the side channel 28 by adjacently arranged impeller blades 2. The gas then flows in the suction channel 44 and re-enters the side channel 28 via the inlet opening 45.
  • FIG Fig. 5 a fourth embodiment is described. Identical parts are given the same reference numbers as in the previous embodiments. Parts that are structurally different but functionally identical have the same reference numerals with a "d" after them.
  • the outer wall 42d of the interrupter 39d which also forms the flow guide wall 37, extends parallel to an absolute velocity vector or to an absolute velocity direction 46 of the gas flowing immediately upstream to the interrupter 39d at the flow point P.
  • the absolute velocity vector 46 is determined by adding the circumferential velocity of the The impeller 3 is obtained about the longitudinal center axis 5 and the relative speed of the gas radially outwards with respect to the longitudinal center axis 5.
  • angle e which is preferably between 15 ° and 40 °, more preferably between 20 ° and 30 °.
  • the gas outlet connector 31 can widen in the flow direction 32.
  • FIG Fig. 6 a fifth embodiment of the invention is described. Identical parts are given the same reference numerals as in the previous embodiments. Parts that are structurally different but functionally identical have the same reference numerals followed by an "e”.
  • the discharge channel 43e which provides a flow connection between the side channel 28 and the gas outlet nozzle 31 manufactures.
  • the discharge channel 43e extends radially or essentially radially with respect to the longitudinal center axis 5.
  • the suction volume flow is thus dependent on the circumferential speed of the impeller, the cross-sectional area of the side channel on the pressure side, the pressure ratio over the side channel fan and the diameter of the Impeller at the impeller-blade base as well as the outer diameter of the impeller.
  • a dead space trough 47 extends from the gas outlet connection 31 or the outer wall 42e of the interrupter 39e.
  • the discharge channel 43e opens into the dead space trough 47.
  • an automatic valve plate 49 is fastened to the interrupter 39e via at least one fastening means 48, which, in its closed position, closes the discharge channel 43e at its downstream end area opposite its inlet opening 56. In the open position, the valve plate 49 is lifted from the interrupter 39e, at least in some areas, and thus releases the discharge channel 43e at least in some areas for the gas.
  • the gas outlet connector 31 In the area of the dead space trough 47, the gas outlet connector 31 thus has an expanded cross-sectional area.
  • a gas dead space region is created in the dead space trough 47.
  • the pressure of the gas is then reduced in the dead space trough 47, so that when the valve plate 49 is open, gas is sucked out of the impeller cell 50 which is currently adjacent to the discharge channel 43e.
  • the valve plate 49 In its closed position, the valve plate 49 prevents the gas from flowing back unintentionally from the gas outlet connector 31 or the dead space trough 47 into the discharge channel 43e or the side channel 28.
  • valve plate 49 can also in the embodiment according to Fig. 6 be present without dead space trough 47.
  • the suction volume flow is thus dependent on the circumferential speed of the impeller, the cross-sectional area of the side channel on the pressure side, the pressure ratio over the side channel blower, the diameter of the impeller at the impeller-blade base and the outer diameter of the impeller as well as the cross-sectional area of the vena contracta of the Venturi nozzle in the Gas outlet connection dependent.
  • FIG Fig. 7 a sixth embodiment of the invention is described. Identical parts are given the same reference numerals as in the previous embodiments. Parts that are structurally different but functionally identical have the same reference numerals with an "f" after them.
  • the side channel blower 1f has a flow reducing projection 51 which jumps into the gas outlet connection 31.
  • the discharge channel 43f also penetrates the Flow reduction projection 51.
  • a valve plate 49 is preferably arranged on the flow reduction projection 51 again via at least one fastening means 48.
  • the gas outlet connector 31 has a reduced flow cross-section, so that there is a particularly high flow velocity of the conveyed gas. Conversely, there is consequently a reduced pressure there, so that gas is sucked out of the impeller cell 50 which is just adjacent to the discharge channel 43f via the discharge channel 43f into the gas outlet connection 31.
  • a Venturi nozzle or arrangement is created in this way.
  • FIG Fig. 8 a seventh embodiment is described. Identical parts are given the same reference numerals as in the previous embodiments. Parts that are structurally different but functionally identical have the same reference numerals with a "g" after them.
  • the interrupter 39g there is at least one stress-relieving groove 52 which starts from the side channel 28. Between an upstream starting point 53 of the expansion groove 52 and an axial or circumferential impeller cell opening 54, there is preferably a distance x which corresponds to at least 1.5 times the distance r between adjacent impeller blades 2 around the longitudinal center axis 5. In the conveying direction 6, the radial depth t of the relaxation groove 52 gradually increases in relation to the longitudinal center axis 5.
  • the angle e of the relaxation groove 52 is favorably based on the pressure ratio p Z / p 1 and the circumferential speed u of the impeller, where pz is the prevailing pressure in the impeller cells 50 and p 1 is the suction pressure of the side-channel blower is.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (6)

  1. Machine à canal latéral, comprenant
    a) un boîtier (4),
    b) un canal latéral (28) se trouvant dans le boîtier (4), sensiblement annulaire, servant à guider un gaz,
    c) au moins une tubulure d'entrée de gaz (29),
    d) au moins une ouverture d'entrée de gaz (34) se trouvant en communication fluidique avec le canal latéral (28), réalisée dans le boîtier (4), servant à guider le gaz hors de l'au moins une tubulure d'entrée de gaz (29) dans le canal latéral (28),
    e) au moins une ouverture de sortie de gaz (33) disposée dans le boîtier (4), servant à évacuer le gaz hors du canal latéral (28),
    f) au moins une tubulure de sortie de gaz (31) se raccordant à l'au moins une ouverture de sortie de gaz (33),
    g) une roue mobile (3) pouvant tourner dans le boîtier (4) autour d'un axe de rotation (5), avec des aubes de roue mobile (2) disposées dans le canal latéral (28), délimitant des cellules de roue mobile (50), servant au refoulement du gaz se trouvant dans les cellules de roue mobile (50) dans le canal latéral (28) de l'au moins une ouverture d'entrée de gaz (34) à l'au moins une ouverture de sortie de gaz (33),
    h) au moins un disjoncteur (39e ; 39f) disposé entre l'au moins une ouverture d'entrée de gaz (34) et l'au moins une ouverture de sortie de gaz (33), servant à empêcher un transport du gaz de l'au moins une ouverture de sortie de gaz (33) à l'au moins une ouverture d'entrée de gaz (34), et
    i) dans l'au moins un disjoncteur (39e; 39f), au moins un canal d'évacuation (43e ; 43f) servant à évacuer le gaz piégé dans au moins une des cellules de roue mobile (50) adjacentes précisément par rapport à l'au moins un canal d'évacuation (43e ; 43f) hors du canal latéral (28),
    caractérisé en ce que
    le canal d'évacuation guide le gaz dans l'au moins une tubulure de sortie de gaz (31) et qu'est présent au moins un ensemble Venturi servant à aspirer le gaz piégé dans au moins une des cellules de roue mobile (50) adjacentes précisément par rapport à l'au moins un canal d'évacuation (43e ; 43f) hors du canal latéral (28) dans l'au moins une tubulure de sortie de gaz (31) par l'intermédiaire de l'au moins un canal d'évacuation (43e; 43f).
  2. Machine à canal latéral selon la revendication 1, caractérisée par au moins un clapet (49), en particulier un clapet à disque, associé à l'au moins un canal d'évacuation (43e ; 43f), servant à empêcher un écoulement de reflux du gaz hors de l'au moins une tubulure de sortie de gaz (31) dans le canal latéral (28).
  3. Machine à canal latéral selon la revendication 1 ou 2, caractérisée par au moins une cavité d'espace mort (47) disposée au niveau du disjoncteur (39e), servant à aspirer le gaz piégé dans au moins une des cellules de roue mobile (50) adjacentes précisément par rapport à l'au moins un canal d'évacuation (43e) hors du canal latéral (28) dans l'au moins une tubulure de sortie de gaz (31) par l'intermédiaire de l'au moins un canal d'évacuation (43e).
  4. Machine à canal latéral selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un rétrécissement de section transversale nécessaire pour former l'ensemble Venturi est disponible dans l'au moins une tubulure de sortie de gaz (31).
  5. Machine à canal latéral selon l'une quelconque des revendications précédentes, caractérisée en ce que le canal d'évacuation (43e) établit une communication fluidique entre le canal latéral (28) et l'au moins une tubulure de sortie de gaz (31).
  6. Machine à canal latéral selon l'une quelconque des revendications précédentes, caractérisée en ce que l'au moins une tubulure d'entrée de gaz (29) se raccorde de manière sensiblement tangentielle au canal latéral (28) pour introduire de manière sensiblement tangentielle le gaz dans le canal latéral (28).
EP16738825.5A 2015-07-17 2016-07-15 Machine à canal latéral (compresseur, pompe à vide, ou ventilateur) avec un conduit de purge dans le barrage Active EP3325812B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP20205155.3A EP3792495A1 (fr) 2015-07-17 2016-07-15 Machine à canal latéral (compresseur, pompe à vide ou ventilateur) avec conduit de décharge dans le barrage

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015213549.7A DE102015213549A1 (de) 2015-07-17 2015-07-17 Seitenkanal-Maschine
PCT/EP2016/066918 WO2017013021A1 (fr) 2015-07-17 2016-07-15 Machine à canal latéral (compresseur, pompe à vide ou soufflante) munie d'un canal de prélèvement dans le déflecteur

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP20205155.3A Division EP3792495A1 (fr) 2015-07-17 2016-07-15 Machine à canal latéral (compresseur, pompe à vide ou ventilateur) avec conduit de décharge dans le barrage

Publications (2)

Publication Number Publication Date
EP3325812A1 EP3325812A1 (fr) 2018-05-30
EP3325812B1 true EP3325812B1 (fr) 2020-11-11

Family

ID=56411666

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EP16738825.5A Active EP3325812B1 (fr) 2015-07-17 2016-07-15 Machine à canal latéral (compresseur, pompe à vide, ou ventilateur) avec un conduit de purge dans le barrage
EP20205155.3A Withdrawn EP3792495A1 (fr) 2015-07-17 2016-07-15 Machine à canal latéral (compresseur, pompe à vide ou ventilateur) avec conduit de décharge dans le barrage

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Country Link
US (4) US10767654B2 (fr)
EP (2) EP3325812B1 (fr)
JP (1) JP2018520295A (fr)
CN (1) CN108138785A (fr)
CA (1) CA2992672A1 (fr)
DE (1) DE102015213549A1 (fr)
ES (1) ES2846857T3 (fr)
WO (1) WO2017013021A1 (fr)

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WO2019120633A1 (fr) * 2017-12-21 2019-06-27 Pierburg Gmbh Compresseurs à canal latéral, en particulier compresseurs d'air secondaires pour un moteur à combustion interne
US11598347B2 (en) * 2019-06-28 2023-03-07 Trane International Inc. Impeller with external blades
CN110425157B (zh) * 2019-09-04 2023-12-15 宁波纽新克电机有限公司 一种高效型混气离心风机
JP7342574B2 (ja) * 2019-09-27 2023-09-12 株式会社島津製作所 真空ポンプ
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US11624405B1 (en) * 2020-06-23 2023-04-11 Airtech Group, Inc. Bearing housing and bearing subassembly for use in side channel blower and side channel blower employing same

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Also Published As

Publication number Publication date
ES2846857T3 (es) 2021-07-29
EP3792495A1 (fr) 2021-03-17
US11248615B2 (en) 2022-02-15
CA2992672A1 (fr) 2017-01-26
CN108138785A (zh) 2018-06-08
JP2018520295A (ja) 2018-07-26
DE102015213549A1 (de) 2017-01-19
US20180202447A1 (en) 2018-07-19
EP3325812A1 (fr) 2018-05-30
US12078179B2 (en) 2024-09-03
US20220228595A1 (en) 2022-07-21
US10767654B2 (en) 2020-09-08
US11536281B2 (en) 2022-12-27
WO2017013021A1 (fr) 2017-01-26
US20210095677A1 (en) 2021-04-01
US20230193907A1 (en) 2023-06-22

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