EP1672222B1 - Seitenkanalverdichter - Google Patents

Seitenkanalverdichter Download PDF

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Publication number
EP1672222B1
EP1672222B1 EP05027844A EP05027844A EP1672222B1 EP 1672222 B1 EP1672222 B1 EP 1672222B1 EP 05027844 A EP05027844 A EP 05027844A EP 05027844 A EP05027844 A EP 05027844A EP 1672222 B1 EP1672222 B1 EP 1672222B1
Authority
EP
European Patent Office
Prior art keywords
lateral channel
rib
compressor according
channel compressor
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.)
Not-in-force
Application number
EP05027844A
Other languages
English (en)
French (fr)
Other versions
EP1672222A2 (de
EP1672222A3 (de
Inventor
Rudi Dittmar
Mario Kempf
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
Publication of EP1672222A2 publication Critical patent/EP1672222A2/de
Publication of EP1672222A3 publication Critical patent/EP1672222A3/de
Application granted granted Critical
Publication of EP1672222B1 publication Critical patent/EP1672222B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status 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
    • 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
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • F04D17/168—Pumps specially adapted to produce a vacuum

Definitions

  • the invention relates to a lateral channel compressor.
  • gas that is to be compressed is set moving helically in at least one annular lateral channel by means of a rotating impeller which is actuated by a driving aggregate, in the process being compressed from an intake towards a pressure joint.
  • the gas that is aspirated at the intake is entrained by reason of the impeller rotating in the lateral channel, then set moving helically in the peripheral direction and ejected after approximately 360° by way of the pressure joint.
  • the lateral channel compressor can be used as a compressor as well as a vacuum pump. Owing to the simple principle of compression, the lateral channel compressor is rather solid, being used preferably in cases where high gas flow rates are involved. Special advantages of the lateral channel compressor reside in the lack of maintenance work, oil-free compression, low noises and extreme lifetime.
  • US 6,779,968 B1 and EP 0 863 314 A1 disclose a side channel compressor, wherein the cross-section of the side channel diminishes between the inlet port and the outlet port.
  • a lateral channel compressor comprising the features of claim 1.
  • the lateral channel compressor possesses an impeller which is arranged in a casing for rotation about an axial axis, in the radial direction on the side of its end having a supporting ring with a plurality of blades which are disposed in the peripheral direction and are located in a lateral channel.
  • the lateral channel has an elliptical cross-sectional geometry, tapering from an aspiration side to a pressure side.
  • the elliptical cross-sectional geometry is configured by an inside wall area of the casing as well as a sectional area of the supporting ring.
  • the special advantage of this configuration resides in the combination of the elliptical cross-sectional geometry and the tapering cross-sectional surface of the lateral channel.
  • the tapering cross-sectional surface of the lateral channel aids in the compression of the gas, which improves the degree of efficiency.
  • Special significance resides in that the elliptical cross-sectional geometry is formed by the casing as well as the supporting ring. As a result, the lateral channel is enclosed almost fully, having a defined elliptical geometry. The clearance between two impeller blades that succeed one another in the peripheral direction therefore has a closed elliptical cross-sectional geometry. This works in support of a configuration, as free from losses as possible, of the helical flow (circulating flow) of the gas inside the lateral channel, largely precluding any turbulences that might affect the efficiency.
  • the inside wall area of the casing opposite the supporting ring as seen in the radial direction, comprises a sectional area which retracts inwards into the lateral channel.
  • the inside wall area of the casing comprises in particular approximately three quarters of the wall area of the elliptical cross-sectional geometry. Therefore, the lateral channel, for its major part, is defined by the stationary casing. Only a comparatively small area is defined by the rotating impeller and the supporting ring, which is advantageous, not least with a view to the mechanical stability of the rotating impeller.
  • the supporting ring For as closed an elliptical cross-sectional geometry as possible that is de-fined all over by a wall area, an appropriate development makes provision for the supporting ring to comprise a rib that extends in the radial direction as far as to the opposite inside wall area of the casing.
  • the supporting ring by the rib, separates from one another two lateral channels which are disposed side by side in the axial direction. Consequently, the lateral channel compressor is a double-entry compressor in this initial embodiment.
  • the two lateral channels will be called entries in the following.
  • the ribs first tapers in the radial direction and then widens again. Therefore, the rib, as seen cross-sectionally, has a constriction or necking i.e., it is concavely curved towards the lateral channel. In this case, the rib is preferably symmetrical of the two side by side entries.
  • the wall area that is defined by the rib passes as homogeneously as possible into the wall area, defined by the casing, of the lateral channel.
  • the rib face on the side of the end as seen in the radial direction and the frontal flanks of the impeller blades substantially are in alignment i.e., they are substantially located on a joint rotational surface. Therefore, there are no irregularities where the blade flanks pass into, or are connected with, the rib.
  • a gap between the rib and the inside wall area opposite thereto is comparatively wide with no lint or dust accumulating between the rotating impeller and the casing.
  • the width of the gap is preferably in the range of 1 mm to 3 mm or, respectively, 0.3 % and 1.5% of the outside diameter of the rib.
  • the rib on its radial face, possesses at least one groove and preferably two grooves that are displaced one in relation to the other by 180°. They extend in the axial direction. As the case may be, these grooves may also be askew of the axial direction by up to 45°.
  • the impeller blades lap over at least half the depth of the lateral channel.
  • the depth of the lateral channel is understood to be the maximal clear inner width of the lateral channel as seen in the axial direction.
  • the flanks of the impeller blades coincide with one of the two semiaxes of the elliptical cross-sectional surface. As the case may be, this semiaxis, which runs in the radial direction, also extends within the impeller blades.
  • the impeller blades are curved in the direction of their radial extension. This curvature aids in the forming of the circulatory flow, by a favourable component acting in the radial direction on the flow that forms.
  • the gas flows in the radial direction from the impeller clearance into the lateral channel.
  • a preferred embodiment provides that approximately half the cross-sectional surface of an aspirating hole that opens out into the lateral channel laps over the impeller blades. This means that the impeller blades run past approximately half the aspirating hole, with the remaining half of the aspirating hole opening into a sectional area of the lateral channel the impeller blades do not pass.
  • the aspirating hole is made to have a radius that corresponds approximately to the height of the impeller blades.
  • the lateral channel compressor comprises a two-entry lateral channel 2 with two entries 2A, 2B that adjoin in the axial direction 4.
  • the lateral channel compressor possesses a two-piece casing which includes a casing member 6 and a cover 8.
  • the casing 6, 8 houses an impeller 12 rotatably about an axis of rotation that extends in the axial direction 4.
  • the impeller 12 is operated by way of a drive shaft (not shown) and a driving motor.
  • the impeller 12 extends in the radial direction 14, comprising a hub 16 that is followed by a supporting ring 18 which a plurality of blades 20 are disposed on in the peripheral direction or direction of rotation of the impeller 12.
  • the supporting ring 18 stands out from the hub 16 bilaterally in the axial direction 4. It has a rib 22 that runs in the radial direction 14, separating the entries 2A, 2B from each other and defining them one in relation to the other. Between the casing 6, 8 and the impeller 12, provision is made for a gap which is sealed by a sealing arrangement 24 which is fixed by screws 26 in the axial direction 4.
  • the elliptical cross-sectional surface of the two entries 2A, 2B is defined by an inside wall area 28 of the casing members 2, 6 as well as by a corresponding wall area of the rib 22.
  • the inside wall area 28 as well as the rib 22 constitute curved surfaces, producing the elliptical cross-sectional contour.
  • the curvatures of the inside wall area 28 and of the rib 22 are selected and mutually fitted in such a way that the wall areas pass into one another in as homogeneous and jointless a manner as possible.
  • the individual wall areas therefore are substantially in alignment with one another.
  • a sectional area 30 of the casing member 6 - either as a integral component of the casing member 6 or as a separate insert - which simultaneously constitutes a part of the inside wall area 28 for both entries 2A, 2B.
  • the sectional area 30 is disposed opposite the rib 22 in the radial direction 14.
  • the elliptical cross-sectional geometry is largely determined by the casing 6,8.
  • the sectional area 30 helps attain that the lateral channel 2 is continued above the frontal definition of the impeller blades 20 so that gas, which is to be compressed, may also flow into the lateral channel 2 substantially in the radial direction, producing a circulation 32 as roughly outlined by the arrow.
  • the long semiaxis 34A of the elliptical cross-sectional surface extends in the radial direction 14 and aligns with a respective flank 36 of the impeller blades 20.
  • the exemplary embodiment shows the short semiaxis 34B to be perpendicular to the long semiaxis 34A, consequently running in the axial direction 4.
  • the maximal extension along the long semiaxis 34A defines the height h of the lateral channel and the maximal extension in the direction of the short semiaxis 34B defines the depth t of the lateral channel i.e., the depth of the respective entry 2A, 2B.
  • the rib 22 extends for approximately three quarters of the height h of the lateral channel.
  • the face 38, on the side of the end in the radial direction 14, of the rib 10 is spaced from the sectional area 30 by a gap 40.
  • the gap 40 is comparatively wide, preventing dust or lint from accumulating in this area.
  • the face 38 is in at least near alignment with the frontal flank 39 of the impeller blades 20, the frontal flanks 39 and the face 38 being substantially peripherally level.
  • the impeller blades 20 are curved, having a curved blade pan 42 which is mounted on a blade footing 44.
  • the pan 42 passes without any edges into the blade footing 44.
  • the blade pan 42 is oriented in relation thereto and, consequently in relation to the horizontal by an angle ⁇ 1 .
  • the blade pan 42 is oriented in relation to the horizontal by another angle ⁇ 2 which is in approximately the same range as the angle ⁇ 1 , being approximately in an order of magnitude of 60°.
  • the blade pan 42 itself has a radius of curvature R.
  • FIG. 4 which offers a view into the interior of the casing member 6 without the cover 8
  • an intake 52 and a pressure joint 54 are connected to the casing member 6.
  • the impeller 12 (not shown in this case) rotates in the direction of rotation 50, compressing the gas, which has been sucked by the intake 52, continuously towards the pressure joint 54 and ejecting the compressed gas via the pressure joint 54.
  • An interrupter 56 is disposed between both, the intake 52 and the pressure joint 54. They are spaced apart by approximately 60° in the exemplary embodiment.
  • the lateral channel 2 is tapered in the direction of rotation 50 from the intake 52 to the pressure joint 54.
  • the taper is in particular steady and continuous, for example, linear.
  • the reduction of the lateral channel cross-section is selected accordingly, depending on the application and the area of usage.
  • the lateral channel cross-section is reduced, for example, by solely reducing the lateral channel depth t, as shown in particular in Fig. 5 .
  • a total of 3 cuts are set in opposite positions by the lateral channel 2, with one cut in the area of the intake 52 (curve a), one cut approximately in the centre of the lateral channel at 180° (curve b) and one cut at the end of the lateral channel in the area of the pressure joint 54 (curve c).
  • the depth of the lateral channel t is reduced by approximately 1 ⁇ 4.
  • the lateral channel height h can also, or alternatively, be reduced.
  • the reduction of the lateral channel depth t and / or the lateral channel height h is here in particular linear.
  • the depth t or height h is selected appropriately, for example, according to a parabolic or exponential gradient.
  • the lateral channel compressor described here is characterized in particular by the special geometry of the lateral channel 2 with its elliptical cross-sectional geometry and the cross-sectional area which tapers in the direction of rotation 50. These two features create a double-entry lateral channel compressor, which combines the "closed” and the "open” designs for a lateral channel compressor.
  • a closed design is regarded as being a design in which the impeller blades 20 are open solely in the axial direction 4 to the lateral channel 2.
  • an open design three sides of the impeller blades 20 are open to the lateral channel 2.
  • the lateral channel compressor described here combines the two design insofar as the impeller blades 20 are open on their frontal flanks 39 to the lateral channel 2, while at the same time being closed via the rib 22 in their central section to the sectional area 30 (see Fig. 1 ).
  • This special arrangement in particular in connection with the elliptical definition of the lateral channel 2 on almost all sides, achieves a high and consistent degree of efficiency.
  • a lateral channel compressor of this type is therefore particularly useful in cases when speed regulation is required, since the degree of efficiency remains generally constant, regardless of the currently selected speed.
  • the high degree of efficiency is achieved due to the systematic and largely turbulencefree guidance of the flow in order to produce the circulation 32, which is in particular produced by the special geometry of the lateral channel 2 in connection with the geometry of the impeller blades 20.
  • the homogeneous transfer between the rib 22 and the inside wall area 28 is also a contributory factor. Due to the comparatively broad gap 40 ( Fig. 1 ) and the two grooves 46 ( Fig. 3 ), the lateral channel compressor is in addition unaffected by dust and lint.
  • an aspiration opening 58 with which the intake 52 opens into the lateral channel 2 is covered over by the impeller 12 in the area of the impeller blades, as shown as a diagrammatical sketch in Fig. 6 .
  • the radius of the aspiration hole 58 approximately corresponds here to the radial height of the impeller blades 20.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Motor Or Generator Cooling System (AREA)
  • Massaging Devices (AREA)
  • Magnetic Resonance Imaging Apparatus (AREA)

Claims (11)

  1. Seitenkanalverdichter mit
    a. einem in einem Gehäuse (6, 8) angeordneten und um eine axiale Drehachse (48) rotierbar gelagerten Laufrad (12),
    b. welches in Radialrichtung (14) endseitig einen Tragring (18) mit einer Mehrzahl von Laufradschaufeln (20) aufweist,
    c. die sich in einem Seitenkanal (2, 2A, 2B) mit einer elliptischen Querschnittsgeometrie befinden,
    d. wobei der Seitenkanal (2, 2A, 2B) begrenzt ist von einem Innenwandbereich (28) des Gehäuses (6, 8) sowie von einem Teilbereich des Tragrings (19),
    e. wobei die Querschnittsfläche des Seitenkanals (2, 2A, 2B) sich von einer Saugseite zu einer Druckseite verjüngt, dadurch gekennzeichnet, dass
    f. der Innenwandbereich (28) in Radialrichtung (14) gegenüberliegend zum Tragring (18) zur Ausbildung der elliptischen Querschnittsgeometrie einen nach innen gezogenen Teilbereich (30) aufweist.
  2. Seitenkanalverdichter nach Anspruch 1, bei dem der Tragring (18) einen sich in Radialrichtung (14) erstreckenden Steg (22) umfasst, der sich bis zum gegenüberliegenden Innenwandbereich (28) des Gehäuses (6, 8) erstreckt.
  3. Seitenkanalverdichter nach Anspruch 2, bei dem durch den Steg (22) zwei in Axialrichtung (4) nebeneinander angeordnete Fluten (2A, 2B) des Seitenkanals (2, 2A, 2B) ausgebildet und voneinander abgegrenzt sind.
  4. Seitenkanalverdichter nach Anspruch 2 oder 3, bei dem der gekrümmte Steg (22) mit dem gekrümmten Innenwandbereich (28) fluchtet.
  5. Seitenkanalverdichter nach einem der Ansprüche 2 bis 4, bei dem sich der Steg (22) zur Ausbildung der elliptischen Querschnittsgeometrie in Radialrichtung 814) zunächst verjüngt und anschließend wieder erweitert.
  6. Seitenkanalverdichter nach einem der Ansprüche 2 bis 5, bei dem die in Radialrichtung (14) endseitige Stirnfläche (38) des Stegs (22) und die stirnseitigen Schaufelflanken (39) der Laufradschaufeln (20) im Wesentlichen miteinander fluchten.
  7. Seitenkanalverdichter nach einem der Ansprüche 2 bis 6, bei dem zwischen dem Steg (22) und dem gegenüberliegenden Innenwandbereich (28) ein Spalt (40) ausgebildet ist, dessen Breite in etwa im Bereich von 0,3 bis 1,5 % des Außendurchmessers des Stegs liegt.
  8. Seitenkanalverdichter nach einem der Ansprüche 2 bis 7, bei dem der Steg (22) an seiner radialen Stirnfläche (38) zumindest eine Nut (46), vorzugsweise zwei um 180° zueinander versetzt angeordnete Nuten (26) aufweist, die sich in Axialrichtung (4) oder unterer einem Winkel von bis zu 45° schräg zur Axialrichtung erstrecken.
  9. Seitenkanalverdichter nach einem der vorhergehenden Ansprüche, bei dem eine der beiden Halbachsen (34A) der elliptischen Querschnittsfläche des Seitenkanals (2, 2A, 2B) sich in Radialrichtung (14) erstreckt und entlang von Schaufelflanken (36) der Laufradschaufeln (20) oder im Bereich der Laufradschaufeln (20) verläuft.
  10. Seitenkanalverdichter nach einem der vorhergehenden Ansprüche, bei dem die Laufradschaufeln (20) in ihrer radialen Erstreckung gekrümmt sind.
  11. Seitenkanalverdichter nach einem der vorhergehenden Ansprüche, bei dem saugseitig eine Saugöffnung (58) in den Seitenkanal (2, 2A, 2B) mündet, die mir ihrer halben Querschnittsfläche das sich in den Seitenkanal (2, 2A, 2B) erstreckende Laufrad (12) überdeckt.
EP05027844A 2004-12-17 2005-12-19 Seitenkanalverdichter Not-in-force EP1672222B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE202004019506U DE202004019506U1 (de) 2004-12-17 2004-12-17 Seitenkanalverdichter

Publications (3)

Publication Number Publication Date
EP1672222A2 EP1672222A2 (de) 2006-06-21
EP1672222A3 EP1672222A3 (de) 2007-04-04
EP1672222B1 true EP1672222B1 (de) 2009-09-09

Family

ID=35840387

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05027844A Not-in-force EP1672222B1 (de) 2004-12-17 2005-12-19 Seitenkanalverdichter

Country Status (3)

Country Link
EP (1) EP1672222B1 (de)
AT (1) ATE442527T1 (de)
DE (2) DE202004019506U1 (de)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112015003162T5 (de) * 2014-07-09 2017-04-27 Mag Aerospace Industries, Llc Vakuumerzeuger-Strömungsumlenkeinrichtung
DE102015100215B4 (de) 2015-01-09 2021-01-14 Pierburg Gmbh Seitenkanalgebläse für eine Verbrennungskraftmaschine
DE102015100214B4 (de) 2015-01-09 2021-01-14 Pierburg Gmbh Seitenkanalgebläse für eine Verbrennungskraftmaschine
PL3199816T3 (pl) * 2016-01-29 2021-11-29 Cattani S.P.A. Dmuchawa boczno-kanałowa / pochłaniacz z ulepszonym wirnikiem
DE102016222430A1 (de) * 2016-11-15 2018-05-17 Gardner Denver Deutschland Gmbh Seitenkanalverdichter

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19708952A1 (de) * 1997-03-05 1998-09-17 Busch Gmbh K Seitenkanalverdichter mit sich verjüngendem Kanalquerschnitt
DE19913950A1 (de) * 1999-03-26 2000-09-28 Rietschle Werner Gmbh & Co Kg Seitenkanalverdichter

Also Published As

Publication number Publication date
EP1672222A2 (de) 2006-06-21
DE202004019506U1 (de) 2006-04-20
EP1672222A3 (de) 2007-04-04
DE602005016515D1 (de) 2009-10-22
ATE442527T1 (de) 2009-09-15

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