EP3325812A1 - Machine à canal latéral (compresseur, pompe à vide ou soufflante) munie d'un canal de prélèvement dans le déflecteur - Google Patents

Machine à canal latéral (compresseur, pompe à vide ou soufflante) munie d'un canal de prélèvement dans le déflecteur

Info

Publication number
EP3325812A1
EP3325812A1 EP16738825.5A EP16738825A EP3325812A1 EP 3325812 A1 EP3325812 A1 EP 3325812A1 EP 16738825 A EP16738825 A EP 16738825A EP 3325812 A1 EP3325812 A1 EP 3325812A1
Authority
EP
European Patent Office
Prior art keywords
channel
gas
impeller
side channel
gas outlet
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
EP16738825.5A
Other languages
German (de)
English (en)
Other versions
EP3325812B1 (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
Original Assignee
Gardner Denver Deutschland GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gardner Denver Deutschland GmbH filed Critical Gardner Denver Deutschland GmbH
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
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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.
  • Side channel machines are well known in the art. Side channel machines are capable of conveying or compressing gas.
  • Generic side channel machines are known from DE 103 34 950 AI, DE 197 08 953 AI, DE 103 34 812 AI and DE 199 06 515 Cl, for example, known.
  • the invention has for its object to provide a side channel machine, which has a very high efficiency and extremely quiet operation. Furthermore, the side channel machine is a very high
  • Geometry optimization and targeted flow control of the side channel machine improve the performance of at least one performance parameter.
  • the power density, efficiency and / or noise of the side channel engine over conventional side channel machines is improved.
  • the gas to be delivered is preferably air or a technical gas.
  • the side channel machine is preferably as a side channel blower or side channel Compressor executed. It is advantageous if the side channel machine is capable of operating in vacuum and / or compressor operation.
  • 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 arranged spaced from one another in the flow direction of the gas about the axis of rotation. It is advantageous if between these an angle about the axis of rotation of at least 170 ° is present.
  • the impeller is conveniently located with a motor or drive in direct or indirect drive connection.
  • the at least one breaker is preferably mounted on the housing or 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 delivered from the at least one gas inlet port in a direction of flow about the axis of rotation to the at least one gas outlet port located downstream of the at least one gas inlet port.
  • the gas is thus guided essentially annularly in the side channel. It is preferably pressed in the side channel by the centrifugal force occurring radially outward and then back to the radially inner region of the side channel with respect to the axis of rotation where it re-enters impeller cells between adjacent impeller blades and undergoes centrifugal force again.
  • gas inlet openings and exactly one gas outlet opening and exactly one breaker are present.
  • more than two gas inlet openings a plurality of gas outlet openings and / or breakers are provided.
  • the side channel machine has two impeller floods.
  • exactly one gas inlet port is provided, which is designed to divide the gas, in particular evenly, on the two impeller floods.
  • each impeller flood associated with a gas inlet connection.
  • the at least one gas outlet connection connects substantially tangentially to the side channel for substantially tangential discharge of the gas from the side channel. Due to the substantially tangential arrangement of the at least one gas outlet nozzle on the side channel 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 adjoins the side channel in an absolutely tangential manner for the tangential discharge of the gas from the side channel. Conveniently, between an upstream connection of the at least one gas outlet nozzle to the side channel and a downstream outlet of this gas outlet nozzle, an angle about the axis of rotation between 280 ° and 320 °, more preferably between 290 ° and 310 ° before. This embodiment also results in a reduction of the pressure losses.
  • the side channel is delimited by a radially outer cover with respect to the axis of rotation, wherein the at least one gas outlet nozzle is connected to the ceiling essentially without transition and substantially tangentially.
  • the at least one gas outlet connection connects in an absolutely transitionless and tangential manner to a ceiling bounding the side channel radially outwards.
  • the side channel is delimited by a radially inner bottom with respect to the rotation axis, wherein the at least one gas outlet connection connects to the bottom essentially without transition and substantially tangentially.
  • the remarks on the radially outer ceiling are essentially analogous to the dependent claim 5. It is advantageous if the at least one gas outlet connection connects absolutely tangentially and tangentially to a bottom side bounding the side channel radially inwards.
  • a flow cross-section in the at least one gas outlet nozzle in the direction of flow of the gas is at least extended expansively, preferably at least in an upstream beginning region of the at least one gas outlet nozzle opposite flow guide walls of the at least one gas outlet nozzle an expansion angle of at most 1 1 °, preferably at most 9 ° to each other.
  • the at least one gas outlet nozzle has at least one wall, which is radially inner, preferably with respect to the axis of rotation, which runs essentially parallel to an absolute velocity vector of the gas flowing in the side channel downstream of the at least one interrupter ,
  • the at least one breaker which ensures a particularly quiet operation of the side channel machine.
  • the gas thus conveniently passes along the at least one wall of the at least one gas outlet nozzle. It is advantageous if this at least one wall is present at the at least one breaker. It is expedient for the at least one wall to run absolutely parallel to an absolute velocity vector of the gas flowing in the side channel adjacent to the at least one interrupter.
  • a breaker gas mass flow harmless in the at least one gas outlet nozzle is discharged.
  • the at least one discharge channel is advantageously circular in cross section and preferably extends radially with respect to the axis of rotation. In particular, it extends straight.
  • the embodiment of sub claim 3 prevents that at certain operating points of the side channel machine gas unintentionally from the least flows back least a gas outlet in the side channel or the at least one breaker, which would be unfavorable in terms of efficiency and noise. It is advantageous if the at least one valve is arranged on the output side with respect to the flow of the gas at the at least one interrupter.
  • the gas from at least one of the, at least one discharge channel adjacent impeller cells functionally reliable sucked in a simple manner. It is advantageous if the cross-sectional constriction necessary for the formation of the Venturi arrangement is present in the at least one gas outlet nozzle.
  • the gas from at least one of the at least one discharge channel adjacent impeller cells can be sucked functionally reliable in a simple manner.
  • the gas from at least one of the impeller cells adjacent to the at least one discharge channel can be reliably sucked out in a reliable manner.
  • At least one expansion groove extending from the side channel is attached. assigns. Due to the at least one expansion groove, the relaxation sound of the gas, which arises during operation of the side channel machine by the exiting from the impeller cells, tensioned interrupter gas mass flow, can be reduced. Furthermore, useful volume flows can be reduced by blocking an inflow cross section.
  • the embodiment according to the dependent claim 1 1 effectively prevents the formation of noise and turbulence.
  • the at least one gas inlet connection adjoins the side channel in an absolutely tangential manner for the tangential introduction of the gas into the side channel.
  • FIG. 1 is a view of a conventional side channel machine and a flanged to this drive, the side channel machine is shown in longitudinal section, a plan view of a side-channel machine according to the invention according to a first embodiment, a FIG. 2 corresponding plan view of a side channel machine according to the invention according to a second embodiment, a FIG. 2 corresponding plan view of a side channel machine according to the invention according to a third embodiment, a simplified view, which essentially illustrates a gas outlet nozzle, a part of an impeller and a part of a breaker of a side-channel machine according to the invention according to a fourth embodiment, a simplified view corresponding to FIG.
  • FIG. 5 which is a gas outlet nozzle, a part an impeller and a part of a breaker of a side-channel machine according to the invention according to a fifth embodiment
  • a simplified view corresponding to FIG. 5 which essentially comprises a gas outlet nozzle, a part of an impeller and a Part of a breaker of a side channel machine according to the invention illustrated according to a sixth embodiment
  • FIG. 8 is a simplified view corresponding to FIG.
  • FIG. 7 Essentially illustrates a gas outlet nozzle, a part of an impeller and a part of a breaker of a side channel machine according to the invention according to a seventh embodiment.
  • a conventional side-channel blower 1 comprises an impeller 3 provided with impeller blades 2, which rotates in a housing 4 about one
  • Longitudinal axis or rotation axis 5 is rotatably mounted.
  • a conventional drive 7 For the rotary drive of the impeller 3 is a conventional drive 7. The gas is thus conveyed in the housing 4 accordingly.
  • 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 joined together as shown in FIG. 1 and together enclose the rotatably mounted on a drive shaft 10, rotatably driven impeller 3 with the impeller blades 2.
  • the impeller 3 is formed like a disk. It comprises an inner impeller hub 1 1 with a central, circular hub bore 12.
  • the impeller hub 1 1 is formed by an inner, the hub bore 12 radially outwardly limiting hub base 13 and a subsequent thereto, radial, annular hub disc 14 ,
  • the impeller 3 comprises a radially outer support ring 15, which adjoins the outer side of the hub disc 14 and this overlaps on both sides in the direction of the longitudinal central axis 5.
  • the support ring 15 carries distributed in the circumferential direction a plurality of the impeller blades 2, which project radially from the support ring 15.
  • the impeller blades 2 are equidistant from each other. orderly.
  • impeller cells 50 are limited in the circumferential direction.
  • the first housing part 8 has a central hub portion 16 which radially and axially limits a sub-hub receiving space 17.
  • the hub portion 16 is penetrated by a central shaft bore 18, which opens into the sub-hub receiving space 17.
  • the hub portion 16 is adjoined by an annular side wall 19 that extends radially outward from the hub portion 16.
  • a peripheral channel section 20 adjoins the outside.
  • the hub portion 16, the side wall 19 and the channel portion 20 are formed as a one-piece casting and form the first housing part 8.
  • an annular side wall 24 connects, which extends radially outward.
  • a circumferential channel portion 25 is externally connected.
  • a rolling bearing 26 is arranged for the drive shaft 10.
  • the hub portion 22, the side wall 24 and the channel portion 25 are formed as a one-piece casting and together form the second housing part.
  • the first housing part 8 and the second housing part 9 are connected to one another in the assembled state such that the two partial hub receiving spaces 17, 23 together define a hub receiving space 27 and the two channel sections 20, 25 together form a side channel 28 to promote the gas.
  • the two side walls 19, 24 are spaced parallel to each other.
  • the side channel 28 extends annularly around the longitudinal center axis 5.
  • the second housing part 9 is designed as a housing cover, which is removable from the first housing part 8.
  • a reverse embodiment is alternatively possible.
  • the side channel blower 1 has two gas inlet ports 29. On each housing part 8, 9, a gas inlet port 29 is arranged. Each gas inlet port 29 supplies a flood of the side channel 28. In the operation of the side channel blower 1 via the gas inlet port 29, the gas to be delivered in a flow direction 30 in the side channel blower 1 can be inserted.
  • the side channel blower 1 has a gas outlet port (not shown) formed by the two housing parts 8, 9.
  • the gas outlet nozzle is in flow communication with the side channel 28.
  • the gas inlet port 29 and the gas outlet port extend substantially perpendicular to each other.
  • the hub base 13 of the impeller 3 In the hub receiving space 27 defined by the boss portions 16, 22, in the assembled state of the side duct fan 1 arranged the hub base 13 of the impeller 3, wherein the hub bore 12 is penetrated by the drive shaft 10. Between the mutually spaced side walls 18, 24 of the housing 4, the hub disc 14 of the impeller 3 extends from the hub 13 radially outward.
  • the support ring 15 and the impeller blades 2 are located in the peripheral side channel 28th
  • the side channel blower la of the side channel 28 is spatially limited by a bottom 35 radially inward and by a ceiling 36 radially outward with respect to the longitudinal central axis 5.
  • the base 35 and the cover 36 lie opposite one another and extend at a distance from one another while limiting 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 substantially tangentially secures the side channel 28 via a gas outlet opening 33 in the housing 4a leaves.
  • a gas deflection point in which the conveyed gas slightly radially outward with respect to the Longitudinal axis 5 is deflected.
  • the pumped gas is deflected slightly in the area of the floor 35 as well as in the area of the ceiling 36.
  • the gas outlet 31a extends substantially uniformly in the flow direction 32 of the gas.
  • the at least one gas inlet connection 29a is connected substantially tangentially to the side channel 28, so that the conveyed gas is substantially tangential via at least one gas inlet opening 34 in the housing 4a into the side channel 28 entry.
  • a breaker 39 is arranged in the side channel 28.
  • the breaker 39 has a side wall 40 adjacent to the gas outlet opening 33. Further, the breaker 39 has a radially inner inner wall 41 with respect to the longitudinal central axis 5 and a radially outer outer wall 42 opposite the inner wall 41.
  • Structurally identical components are given the same reference numerals as in the side channel blowers 1, 1a according to FIG. 1 and 2. Functionally similar, but constructively different components receive the same reference numerals with a subordinate "b".
  • the at least one gas inlet connection 29a again connects substantially tangentially to the side channel 28.
  • the gas outlet port 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 port 31b is seamless. This applies both to the radially inner and the radially outer guide of the gas with respect to the longitudinal central axis 5.
  • the gas outlet port 31b widens downstream of the gas outlet port 33.
  • the angle b is at most 9 °.
  • a connection angle c before the longitudinal center axis 5, which is between 290 ° and 310 ° is advantageously.
  • the breaker 39c is penetrated by a discharge passage 43 which extends radially between the inner wall 41 of the breaker 39c and the outer wall 42 of the breaker 39c with respect to the longitudinal center axis 5. As shown in FIG.
  • the discharge channel 43 has a cross-sectional area A.
  • the discharge channel 43 is adjoined on the downstream side, radially inward by a suction channel 44 which opens at a distance from the discharge channel 43 into the side channel 28.
  • the mouth or inlet 45 of the suction channel 44 in the side channel 28 is located approximately opposite to the discharge channel 43.
  • the inlet opening 45 is spaced at an angle d about the longitudinal central axis 5 to the discharge channel 43, which is between 120 ° and 140 °.
  • the suction channel 44 has a larger, in particular substantially 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 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 by corresponding pressure differences, in particular between inlet opening 56 and inlet opening 45.
  • the prevailing pressure at the inlet opening 45 is smaller than at the inlet opening 56.
  • the impeller cells 50 are spatially limited 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.
  • the outer wall 42d of the breaker 39d which also forms the flow passage wall 37, extends parallel to an absolute velocity vector an absolute velocity direction 46 of the gas flowing immediately upstream of the breaker 39d at the flow point P.
  • the absolute velocity vector 46 is by adding the peripheral velocity of the impeller 3 about the longitudinal central axis 5 and the relative velocity of the gas radially outward with respect to the longitudinal central axis 5.
  • an angle e which is preferably between 15 ° and 40 °, more preferably between 20 ° and 30 °.
  • the gas outlet 31 can expand in the flow direction 32.
  • the discharge channel 43e which establishes a flow connection between the side channel 28 and the gas channel. Outlet 31 produces.
  • the discharge channel 43e extends radially or essentially radially with respect to the longitudinal central axis 5.
  • pu> ⁇ where pu is the prevailing pressure in the impeller cell 50 at the discharge channel 43 e and ⁇ is the prevailing pressure downstream of the discharge channel 43e in the gas outlet port 31, applies to functionally reliable extraction.
  • a discharge of the gas via the discharge channel 43 e from the side channel 28 to the gas outlet nozzle 31 is particularly reliable, even if the following condition is met:
  • AK cross-sectional area of the side channel 28 on the pressure side
  • the intake volume flow is thus of the peripheral speed of the impeller, the cross-sectional area of the side channel on the pressure side, the pressure ratio across the side channel blower and the diameter of the Impeller on the impeller blade foot and the outer diameter of the impeller dependent.
  • a dead space depression 47 emerges from the gas outlet port 31 or the outer wall 42e of the interrupter 39e.
  • the discharge channel 43 e opens into the dead space depression 47.
  • an automatic valve plate 49 is attached to the breaker 39e via at least one fastening means 48, which in its closed position, the discharge channel 43e at the downstream
  • valve plate 49 is at least partially lifted by the breaker 39e and thus releases the discharge channel 43e at least partially for the gas.
  • the gas outlet nozzle 31 thus has an expanded cross-sectional area.
  • a gas dead space area is created during operation of the side channel blower le.
  • a reduced pressure of the gas is then present in the dead space depression 47, so that gas is sucked out of the impeller cell 50 when the valve plate 49 is open, which gas is just adjacent to the discharge channel 43 e.
  • the valve plate 49 prevents in its closed position, an unintentional backflow of the gas from the gas outlet port 31 and the dead space recess 47 in the discharge channel 43 e and the side channel 28th
  • valve plate 49 An embodiment without valve plate 49 is alternatively possible.
  • the valve plate 49 may also be present in the embodiment according to FIG. 6 without dead space depression 47.
  • a discharge of the gas via the discharge channel 43 e from the side channel 28 to the gas outlet nozzle 31 is particularly reliable when the following condition is met:
  • a v Cross-sectional area of venturi vena contracta in the gas outlet port 31
  • the intake flow rate is thus the impeller peripheral speed, the pressure side cross sectional area, the pressure ratio across the side channel blower, and the impeller blade foot diameter and the outside diameter of the impeller as well as the cross-sectional area of the vena contracta of the venturi in the gas outlet port.
  • the side channel blower 1f has, instead of the dead space depression 47 at the interrupter 39f, a flow reduction protrusion 51 that jumps into the gas outlet 31.
  • the discharge channel 43f also penetrates the Flow reduction projection 51.
  • a valve plate 49 is again arranged on the flow reduction projection 51 via at least one fastening means 48.
  • the gas outlet nozzle 31 has a reduced flow cross section, so that there is a particularly high flow velocity of the delivered gas.
  • 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 nozzle 31. It is virtually created a Venturi nozzle or arrangement.
  • the breaker 39 g is at least one expansion groove 52, which extends 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, a distance x is preferably present which corresponds to at least 1.5 times the spacing r of adjacent impeller blades 2 about the longitudinal central axis 5 relative to one another , In the conveying direction 6, the radial depth t of the expansion groove 52 gradually increases in relation to the longitudinal central axis 5.
  • the angle e of the expansion groove 52 is favorably governed by the pressure ratio pz / pi and the peripheral speed u of the impeller, where pz is the prevailing pressure in the impeller cells 50 and pi is the suction pressure of the side duct fan is.
  • the at least one expansion groove 52 can then be dimensioned according to the known laws of the "Prandtl-Meyer corner flow".

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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)

Abstract

L'invention concerne une machine à canal latéral qui présente un carter (4a), un canal latéral (28) se trouvant dans le carter (4a) pour le guidage d'un gaz, et au moins une ouverture d'admission de gaz (34) ménagée dans le carter (4a) et en communication fluidique avec le canal latéral (28). La machine à canal latéral présente par ailleurs au moins une tubulure d'admission de gaz (29a) se raccordant à la ou aux ouvertures de sortie de gaz (34). La machine à canal latéral comprend en outre au moins une ouverture d'échappement de gaz (33) et au moins une tubulure d'échappement de gaz (31a) se raccordant à la ou aux ouvertures d'échappement de gaz (33). La machine à canal latéral présente également une roue à aubes rotative dans le carter (4a), comportant des aubes de roue agencées dans le canal latéral (28) et délimitant des cellules de roue à aubes pour le refoulement du gaz se trouvant dans les cellules de roue à aubes de ou des ouvertures d'admission de gaz (34) vers la ou les ouvertures d'échappement de gaz (33). La machine à canal latéral présente également au moins un élément d'interruption (39) agencé entre la ou les ouvertures d'admission de gaz (34) et la ou les ouvertures d'échappement de gaz (33).
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 true EP3325812A1 (fr) 2018-05-30
EP3325812B1 EP3325812B1 (fr) 2020-11-11

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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
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

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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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US (4) US10767654B2 (fr)
EP (2) EP3792495A1 (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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EP3728860B1 (fr) * 2017-12-21 2021-10-13 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
DE102020205531A1 (de) 2020-04-30 2021-11-04 Mahle International Gmbh Seitenkanalverdichter zum Verdichten von Gas
DE102020205533A1 (de) 2020-04-30 2021-11-04 Mahle International Gmbh Seitenkanalverdichter zum Verdichten eines Gases
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
US11536281B2 (en) 2022-12-27
WO2017013021A1 (fr) 2017-01-26
DE102015213549A1 (de) 2017-01-19
EP3325812B1 (fr) 2020-11-11
US20180202447A1 (en) 2018-07-19
US20220228595A1 (en) 2022-07-21
US11248615B2 (en) 2022-02-15
CN108138785A (zh) 2018-06-08
CA2992672A1 (fr) 2017-01-26
ES2846857T3 (es) 2021-07-29
US20230193907A1 (en) 2023-06-22
JP2018520295A (ja) 2018-07-26
US20210095677A1 (en) 2021-04-01
EP3792495A1 (fr) 2021-03-17
US10767654B2 (en) 2020-09-08

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