EP2993357B1 - Radial compressor stage - Google Patents
Radial compressor stage Download PDFInfo
- Publication number
- EP2993357B1 EP2993357B1 EP15179255.3A EP15179255A EP2993357B1 EP 2993357 B1 EP2993357 B1 EP 2993357B1 EP 15179255 A EP15179255 A EP 15179255A EP 2993357 B1 EP2993357 B1 EP 2993357B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- stator
- flow
- diffuser
- impeller
- side guide
- 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.)
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Links
- 230000005284 excitation Effects 0.000 description 16
- 230000001052 transient effect Effects 0.000 description 3
- 230000007246 mechanism Effects 0.000 description 2
- 238000009827 uniform distribution Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Images
Classifications
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- 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
- F04D29/44—Fluid-guiding means, e.g. diffusers
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- 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
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
- F04D29/444—Bladed diffusers
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- 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
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
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- 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
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
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- 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
- F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations
Definitions
- the invention relates to a radial compressor stage for a radial compressor according to the Oberbergriff of claim 1.
- each radial compressor stage of a radial compressor comprises an impeller rotating with respect to a stator, the impeller comprising a hub and a plurality of rotor-side impeller blades.
- Each impeller vane of the impeller has a flow entrance edge and a flow exit edge, wherein a suction side, a pressure side, and an outer surface facing the stator extend between the flow entrance edge and the flow exit edge of each impeller vane, the outer surface of the respective impeller vane adjacent to the stator and sealing against the stator vane Stator is used.
- Such an impeller of a centrifugal compressor in which the outer surfaces of the impeller blades indirectly adjacent to the stator, has no shroud and is also referred to as an open impeller.
- the impeller blades are positioned in an impeller flow passage delimited by the hub of the impeller and the stator.
- the centrifugal compressor stage includes a diffuser positioned downstream of the impeller having a plurality of stator vanes.
- Each vane of the diffuser has a flow inlet edge and a flow outlet edge, extending between the flow inlet edge and the flow outlet edge of each vane a suction side and a pressure side extends.
- the vanes are positioned in a diffuser flow channel defined by the stator. From the DE 195 02 802 C2 can be seen that between the impeller and the stator of the radial compressor stage shown there is formed a so-called Radreteraum, namely between a rear side of the impeller and the stator. This wheel side space is connected to an intermediate flow passage extending between the impeller flow passage and the diffuser flow passage.
- Another radial compressor stage with such a Radierraum is from the DE 10 2007 019 264 A1 known.
- From the EP 2 014 925 A1 is a radial compressor stage with a diffuser known, in which the angular distance of flow inlet edges of two adjacently arranged guide elements is different from the angular distance of flow inlet edges of two other adjacently arranged guide elements.
- the JP 2004 100 553 A discloses an arrangement of stator vanes which are rotatable about an axis of rotation.
- the DE 41 26 907 A1 discloses a diffuser having first stationary stator vanes and second variable stator vanes. Also, the document discloses a bladed diffuser having circumferentially different flow cross sections.
- the WO 2009/012990 A1 discloses a vaneless diffuser having a radially varying flow area.
- the centrifugal compressor stages are exposed to mechanical stimuli and vibrations which can cause damage to the radial compressor stage, in particular to the rotor blades of the impeller of the radial compressor stage.
- mechanical excitations can be based on synchronous excitation mechanisms as well as on asynchronous excitation mechanisms.
- the present invention has the object to provide a radial compressor stage for a centrifugal compressor, which the above Satisfies requirements and therefore a low vibration excitation is exposed in particular by such asynchronous excitations.
- a radial compressor stage according to claim 1.
- the flow inlet edges of the stator vanes of the diffuser lie on a first circular contour, namely such that the flow inlet edges of all the stator vanes have an identical distance to the flow inlet edges of the respective adjacent vanes.
- the flow outlet edges of the stator-side guide vanes of the diffuser lie on a second circular contour, namely such that at at least one first circumferential position the flow exit edge of the respective stator side vane has a different distance from the flow exit edge of at least one adjacent vane than at second circumferential positions.
- a diffuser flow channel section formed between adjacent stator-side guide vanes has a flow cross-section deviating from the diffuser flow channel sections formed at fourth circumferential positions.
- the present invention relates to a centrifugal compressor with at least one radial compressor stage.
- Fig. 1 shows a detail of a radial compressor stage according to the invention in the meridional section, wherein Fig. 2 an axial section through the radial compressor stage of Fig. 1 shows.
- the radial compressor stage of Fig. 1 has an impeller 10 with a plurality of rotor-side impeller blades 11.
- the impeller 10 rotates with respect to a stator 12.
- the stator 12 may be a housing or a stator ring or the like.
- the impeller blades 11 are positioned in an impeller flow channel 13 which is delimited by a rotor-side hub contour 14 and a stator contour 15.
- Each impeller blade 11 has a flow inlet edge 16 and a flow outlet edge 17. Between the flow inlet edge 16 and the flow outlet edge 17 of each impeller blade 11 extends a pressure side, a suction side and radially outside of the impeller blade 11 a stator 12 facing outer surface 18 of the respective impeller blade 11.
- the outer surface 18 of the impeller blade 11 adjacent to the stator 12 is used to seal against the stator 12.
- Such an impeller 10, in which the outer surfaces 18 of the impeller blades 11 adjacent to the stator 12 indirectly, has no shroud and is also referred to as an open impeller.
- a stator-side diffuser 19 is positioned downstream of the impeller 10.
- the diffuser 19 includes a plurality of stator vanes 20.
- the stator vanes 20 of the diffuser 19 are positioned in a diffuser flow channel 21 defined by the stator 12, wherein each of the stator vanes 20 of the diffuser 19 includes a flow entrance edge 22 and a flow exit edge 23.
- an intermediate flow channel 26 extends, via which medium compressed in the radial compressor stage, starting from the impeller 10 in the direction of the diffuser 19 can flow.
- a Radacheraum 28 said Radnerraum 28 according to Fig. 1 is coupled to the intermediate flow passage 26 via a gap 34.
- the invention now relates to such details of a centrifugal compressor stage, with the help of which the risk of transient flow phenomena, which can lead to an asynchronous excitation of the open wheels, can be reduced.
- all flow inlet edges 22 of all stator-side guide vanes 20 of the diffuser 19 lie on a first circular contour 29.
- the flow inlet edges 22 of the stator vanes 20 of the diffuser 19 are located on the first circular contour 29 such that the flow inlet edges 22 of all the stator vanes 20 have an identical spacing from the flow inlet edges 22 of the adjacent vanes 20.
- the flow inlet edges 22 of the guide vanes 20 of the diffuser 19 positioned next to one another in the circumferential direction of the diffuser flow channel 21 are thus distributed identically in the circumferential direction, so that accordingly all flow inlet edges 22 lying on the first circular contour 29 have identical circumferential spacings to adjacent flow inlet edges 22.
- the flow outlet edges 23 of the stator-side guide vanes 20 of the diffuser 19 lie on a second circular contour 30.
- the flow outlet edges 23 of the stator vanes 20 of the diffuser 19 are located on the second circular contour 30, that at least a first circumferential position of the diffuser flow channel 21, the flow outlet edge 23 of the respective stator side vane 20 positioned there to the flow outlet edge of at least one adjacent vane 20 at a different distance than at second circumferential positions of the diffuser flow channel 21.
- no uniform distribution of the flow outlet edges 23 is provided in the circumferential direction of the diffuser flow channel 21, but rather is preferably at the first circumferential positions the uniform distribution of the flow outlet edges 23, which are all on the second circular contour 30, lifted, so as to reduce the risk of transient flow phenomena that can lead to an asynchronous excitation of the open wheels.
- the corresponding flow outlet edge 23 has a different distance to the respective adjacent flow outlet edges 23, however, that at the other circumferential positions the flow outlet edges 23 are equally distributed in terms of their circumferential positions.
- the flow outlet edges 23 in a second extreme case, it is possible for the flow outlet edges 23 to have respective different spacings at all peripheral positions of the diffuser flow channel 21 relative to the respectively adjacent flow outlet edges 23.
- the respective stator-side vanes 20 of the diffuser 19 preferably all have identical second stagger angles.
- the stator vanes 20 positioned at the or each first circumferential position preferably have a first staggering angle deviating from the second staggering angle, in particular ⁇ 10 °, preferably ⁇ 7 °, more preferably ⁇ 5 °, most preferably ⁇ 3 ° ,
- the flow outlet edges 23 of all stator-side guide vanes 20 of the diffuser 19 may have different distances to the respectively adjacent flow outlet edges 23.
- a flow outlet edge 23 "(see dashed line of in Fig. 2 Right vane) in the direction of the pressure side 25 of the respective adjacent vane 20 or a flow outlet edge 23 '(see dashed line of in Fig. 2 left guide blade) are displaced in the direction of the suction side 24 of the respective adjacent guide blade 20 in the circumferential direction, in such a way that as before all flow outlet edges 23 lie on the second circular contour 30.
- Those selected vanes 20, which have a different staggering angle compared to the other stator vanes 20, are characterized in that their staggering angle deviates, in particular by ⁇ 10 °, particularly preferably ⁇ 5 °, from the staggering angles of the remaining vanes 20 of the diffuser 19 ,
- At least one stator-side guide vane 20 of the diffuser 19 between the flow inlet edge 22 and the flow outlet edge 23 has a different curvature, namely a suction side 24 'and a pressure side 25' with respect to the other vanes 20 deviating curvature.
- stator-side guide vanes 20 of the diffuser 19 it is possible for all the stator-side guide vanes 20 of the diffuser 19 to have different curvatures.
- the diffuser flow channel 21 in order to reduce the risk of unsteady flow phenomena that may lead to asynchronous excitation of the open impellers, it is proposed to change at least a third circumferential position of the diffuser flow channel 21 a diffuser flow channel section 33 formed between adjacent stator vanes 20 of the diffuser 19 such that it is the same has a different flow cross-section with respect to the diffuser flow channel sections formed at fourth circumferential positions.
- the respective diffuser flow channel section 33 has a reduced flow cross section, namely the stator side walls 31, 32 delimiting the respective diffuser flow channel section 33, reducing the flow cross section of the respective diffuser flow channel section 33 inwardly are arched into it.
- the respective diffuser flow channel section 33 bounding side walls 31, 32 may be curved into the respective diffuser flow channel section 33 inside. It is also possible at selected circumferential positions the respective diffuser flow channel section with respect to its flow cross section expand, in which case at least one of these side walls 31, 32 is arched outwardly into the stator 12 in.
- the diffuser flow channel sections 33 it is possible for the diffuser flow channel sections 33 to each have different flow cross sections at all circumferential positions of the diffuser flow channel 21.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
Die Erfindung betrifft eine Radialverdichterstufe für einen Radialverdichter gemäß dem Oberbergriff des Anspruchs 1.The invention relates to a radial compressor stage for a radial compressor according to the Oberbergriff of claim 1.
Aus der
Weiterhin ist es aus der
Aus der
From the
Eine weitere Radialverdichterstufe mit einem solchen Radseitenraum ist aus der
Aus der
Die
Die
From the
The
The
Im Betrieb eines Radialverdichters sind die Radialverdichterstufen mechanischen Anregungen und Schwingungen ausgesetzt, welche Schäden an der Radialverdichterstufe, insbesondere an den Laufradschaufeln des Laufrads der Radialverdichterstufe, hervorrufen können. Solche mechanischen Anregungen können auf synchronen Anregungsmechanismen sowie auf asynchronen Anregungsmechanismen beruhen.During operation of a radial compressor, the centrifugal compressor stages are exposed to mechanical stimuli and vibrations which can cause damage to the radial compressor stage, in particular to the rotor blades of the impeller of the radial compressor stage. Such mechanical excitations can be based on synchronous excitation mechanisms as well as on asynchronous excitation mechanisms.
Insbesondere werden durch die Interaktion von rotierenden und stationären Komponenten dreidimensionale und instationäre Strömungsphänomene erzeugt. Unter bestimmten Bedingungen entstehen Druckschwankungen, welche einen in Drehrichtung oder einen in der Drehrichtung entgegengesetzter Richtung umlaufenden Charakter haben. Die Anzahl und die Umlaufgeschwindigkeit dieser Druckschwankungen ist beliebig.In particular, three-dimensional and transient flow phenomena are generated by the interaction of rotating and stationary components. Under certain conditions, pressure fluctuations occur, which have a direction of rotation or of a direction opposite to that in the direction of rotation. The number and the circulation speed of these pressure fluctuations is arbitrary.
Dieses Phänomen ist Grundlage für eine asynchrone Anregung von offenen Laufrädern in Radialverdichtern. Bislang sind keine Methoden bekannt, mit Hilfe derer solchen asynchronen Anregungen gezielt entgegengewirkt werden kann, um eine kritische Schwingungsanregung insbesondere der Laufradschaufeln des Laufrads zu vermeiden.This phenomenon is the basis for asynchronous excitation of open impellers in centrifugal compressors. So far, no methods are known with the aid of which such asynchronous suggestions can be specifically counteracted to avoid a critical vibration excitation in particular of the impeller blades of the impeller.
Es besteht daher Bedarf an einer Radialverdichterstufe für einen Radialverdichter, bei der insbesondere die Laufradschaufeln des Laufrads einer geringen Schwingungsanregung insbesondere durch solche asynchronen Anregungen ausgesetzt sind.There is therefore a need for a radial compressor stage for a radial compressor, in which in particular the impeller blades of the impeller are exposed to a low vibration excitation, in particular by such asynchronous excitations.
Hiervon ausgehend liegt der vorliegenden Erfindung die Aufgabe zugrunde, eine Radialverdichterstufe für einen Radialverdichter zu schaffen, welche die obigen Anforderungen erfüllt und demnach einer geringen Schwingungsanregung insbesondere durch solche asynchronen Anregungen ausgesetzt ist.On this basis, the present invention has the object to provide a radial compressor stage for a centrifugal compressor, which the above Satisfies requirements and therefore a low vibration excitation is exposed in particular by such asynchronous excitations.
Diese Aufgabe wird durch eine Radialverdichterstufe nach Anspruch 1 gelöst. Hiernach liegen die Strömungseintrittskanten der statorseitigen Leitschaufeln des Diffusors auf einer ersten Kreiskontur, nämlich derart, dass die Strömungseintrittskanten aller statorseitigen Leitschaufeln zu den Strömungseintrittskanten der jeweils benachbarten Leitschaufeln einen identischen Abstand aufweisen. Die Strömungsaustrittskanten der statorseitigen Leitschaufeln des Diffusors liegen auf einer zweiten Kreiskontur, nämlich derart, dass an mindestens einer ersten Umfangsposition die Strömungsaustrittskante der jeweiligen statorseitigen Leitschaufel zu der Strömungsaustrittskante mindestens einer benachbarten Leitschaufeln einen anderen Abstand aufweist als an zweiten Umfangspositionen. Ferner weist an mindestens einer dritten Umfangsposition ein zwischen benachbarten statorseitigen Leitschaufeln ausgebildeter Diffusorströmungskanalabschnitt einen gegenüber den an vierten Umfangspositionen ausgebildeten Diffusorströmungskanalabschnitten abweichenden Strömungsquerschnitt auf.This object is achieved by a radial compressor stage according to claim 1. Thereafter, the flow inlet edges of the stator vanes of the diffuser lie on a first circular contour, namely such that the flow inlet edges of all the stator vanes have an identical distance to the flow inlet edges of the respective adjacent vanes. The flow outlet edges of the stator-side guide vanes of the diffuser lie on a second circular contour, namely such that at at least one first circumferential position the flow exit edge of the respective stator side vane has a different distance from the flow exit edge of at least one adjacent vane than at second circumferential positions. Furthermore, at at least one third circumferential position, a diffuser flow channel section formed between adjacent stator-side guide vanes has a flow cross-section deviating from the diffuser flow channel sections formed at fourth circumferential positions.
Mit der Erfindung kann einfach und zuverlässig asynchronen Anregungen von offenen Laufrädern in Radialverdichtern entgegengewirkt werden, wodurch die Schwingungsanregung insbesondere für die Laufradschaufeln des Laufrads der Radialverdichterstufe reduziert werden kann.With the invention asynchronous suggestions of open wheels in radial compressors can be easily and reliably counteracted, whereby the vibration excitation can be reduced in particular for the impeller blades of the impeller of the radial compressor stage.
Bevorzugte Weiterbildungen der Erfindung ergeben sich aus den Unteransprüchen und der nachfolgenden Beschreibung. Ausführungsbeispiele der Erfindung werden, ohne hierauf beschränkt zu sein, an Hand der Zeichnung näher erläutert. Dabei zeigt:
- Fig. 1:
- einen Meridionalschnitt durch eine erfindungsgemäße Radialverdichterstufe nach der Erfindung;
- Fig. 2:
- einen Axialschnitt durch die Radialverdichterstufe der
Fig. 1 ; - Fig. 3:
- einen Axialschnitt durch eine weitere Radialverdichterstufe; und
- Fig. 4:
- einen Meridionalschnitt durch eine weitere Radialverdichterstufe.
- Fig. 1:
- a meridional section through a radial compressor stage according to the invention according to the invention;
- Fig. 2:
- an axial section through the radial compressor stage of
Fig. 1 ; - 3:
- an axial section through another radial compressor stage; and
- 4:
- a meridional section through another radial compressor stage.
Die hier vorliegende Erfindung betrifft einen Radialverdichter mit mindestens einer Radialverdichterstufe.The present invention relates to a centrifugal compressor with at least one radial compressor stage.
Die Radialverdichterstufe der
Gemäß
Zwischen dem Laufströmungskanal 13, in welchem die rotorseitigen Laufradschaufeln 11 des Laufrads 10 positioniert sind, und dem Diffusorströmungskanal 21, in welchem die statorseitigen Leitschaufeln 20 des Diffusors 19 positioniert sind, erstreckt sich ein Zwischenströmungskanal 26, über welchen in der Radialverdichterstufe verdichtetes Medium ausgehend vom Laufrad 10 in Richtung auf den Diffusor 19 strömen kann. Gemäß
Die oben unter Bezugnahme auf
Die Erfindung betrifft nun solche Details einer Radialverdichterstufe, mit Hilfe derer die Gefahr instationärer Strömungsphänomene, die zu einer asynchronen Anregung der offenen Laufrädern führen können, reduziert werden kann.The invention now relates to such details of a centrifugal compressor stage, with the help of which the risk of transient flow phenomena, which can lead to an asynchronous excitation of the open wheels, can be reduced.
Nach der Erfindungliegen alle Strömungseintrittskanten 22 aller statorseitigen Leitschaufeln 20 des Diffusors 19 auf einer ersten Kreiskontur 29.According to the invention, all flow inlet edges 22 of all stator-
Dabei liegen die Strömungseintrittskanten 22 der statorseitigen Leitschaufeln 20 des Diffusors 19 derart auf der ersten Kreiskontur 29, dass die Strömungseintrittskanten 22 aller statorseitigen Leitschaufeln 20 zu den Strömungseintrittskanten 22 der jeweils benachbarten Leitschaufeln 20 einen identischen Abstand aufweisen. Die Strömungseintrittskanten 22 der in Umfangsrichtung des Diffusorströmungskanals 21 gesehen nebeneinander positionierten Leitschaufeln 20 des Diffusors 19 sind demnach in Umfangsrichtung gesehen gleich verteilt, so dass demnach sämtliche Strömungseintrittskanten 22, die auf der ersten Kreiskontur 29 liegen, zu benachbarten Strömungseintrittskanten 22 identische Umfangsabstände aufweisen.In this case, the flow inlet edges 22 of the
Nach der Erfindung ist weiterhin vorgesehen, dass die Strömungsaustrittskanten 23 der statorseitigen Leitschaufeln 20 des Diffusors 19 auf einer zweiten Kreiskontur 30 liegen.According to the invention, it is further provided that the flow outlet edges 23 of the stator-
Dabei liegen die Strömungsaustrittskanten 23 der statorseitigen Leitschaufeln 20 des Diffusors 19 derart auf der zweiten Kreiskontur 30, dass an mindestens einer ersten Umfangsposition des Diffusorströmungskanals 21 die Strömungsaustrittskante 23 der dort positionierten, jeweiligen statorseitigen Leitschaufel 20 zu der Strömungsaustrittskante mindestens einer benachbarten Leitschaufel 20 einen anderen Abstand aufweist als an zweiten Umfangspositionen des Diffusorströmungskanals 21.In this case, the flow outlet edges 23 of the
Im Bereich der Strömungsaustrittskanten 23 ist demnach in Umfangsrichtung des Diffusorströmungskanals 21 gesehen keine Gleichverteilung der Strömungsaustrittskanten 23 vorgesehen, vielmehr ist vorzugsweise an den ersten Umfangspositionen die Gleichverteilung der Strömungsaustrittskanten 23, die alle auf der zweiten Kreiskontur 30 liegen, aufgehoben, um so der Gefahr instationärer Strömungsphänomene, die zu einer asynchronen Anregung der offenen Laufrädern führen können, zu reduzieren.Accordingly, in the area of the flow outlet edges 23, no uniform distribution of the flow outlet edges 23 is provided in the circumferential direction of the diffuser flow channel 21, but rather is preferably at the first circumferential positions the uniform distribution of the flow outlet edges 23, which are all on the second
Nach der Erfindung ist es in einem ersten Extremfall möglich, dass ausschließlich an einer einzigen Umfangspositionen des Diffusorströmungskanals 21 die entsprechende Strömungsaustrittskante 23 einen anderen Abstand zu den jeweils benachbarten Strömungsaustrittskanten 23 aufweist, dass hingegen an den anderen Umfangspositionen die Strömungsaustrittskanten 23 hinsichtlich ihrer Umfangspositionen gleichverteilt sind.According to the invention, it is possible in a first extreme that only at a single circumferential position of the diffuser flow channel 21, the corresponding
Ebenso ist es nach der Erfindung in einem zweiten Extremfall möglich, dass an allen Umfangspositionen des Diffusorströmungskanals 21 die Strömungsaustrittskanten 23 zu den jeweils benachbarten Strömungsaustrittskanten 23 jeweils unterschiedliche Abstände aufweisen.Likewise, according to the invention, in a second extreme case, it is possible for the flow outlet edges 23 to have respective different spacings at all peripheral positions of the diffuser flow channel 21 relative to the respectively adjacent flow outlet edges 23.
An den zweiten Umfangspositionen des Diffusorströmungskanals 21 weisen die jeweiligen statorseitigen Leitschaufeln 20 des Diffusors 19 vorzugsweise alle identische, zweite Staffelungswinkel auf.At the second circumferential positions of the diffuser flow channel 21, the respective stator-
Die an der oder jeder ersten Umfangsposition positionierten statorseitigen Leitschaufeln 20 hingegen weisen vorzugsweise einen ersten Staffelungswinkel auf, der vom zweiten Staffelungswinkel abweicht, insbesondere um ±10°, bevorzugt um ±7°, besonders bevorzugt um ±5°, meist bevorzugt um ±3°.The stator vanes 20 positioned at the or each first circumferential position, on the other hand, preferably have a first staggering angle deviating from the second staggering angle, in particular ± 10 °, preferably ± 7 °, more preferably ± 5 °, most preferably ± 3 ° ,
Nach der hier vorliegenden Erfindung wird demnach vorgeschlagen, zur Reduzierung der Gefahr instationärer Strömungsphänomene, die zu einer asynchronen Anregung der offenen Laufrädern führen können, die Strömungsaustrittskanten 23 ausgewählter statorseitiger Leitschaufeln 20 des Diffusors 19 in Umfangsrichtung zu versetzen, vorzugsweise unter Aufhebung bzw. Unterbrechung der sonst in Umfangsrichtung des Diffusorströmungskanals 21 gesehen gleichverteilten Strömungsaustrittskanten 23.According to the present invention, it is therefore proposed to reduce the risk of unsteady flow phenomena leading to an asynchronous flow Excitation of the open wheels may cause the flow outlet edges 23 of selected stator-
In einem Extremfall können die Strömungsaustrittskanten 23 aller statorseitiger Leitschaufeln 20 des Diffusors 19 zu den jeweils benachbarten Strömungsaustrittskanten 23 unterschiedliche Abstände aufweisen.In an extreme case, the flow outlet edges 23 of all stator-
Wie
Dies entspricht einer Veränderung des Staffelungswinkels der statorseitigen Leitschaufeln 20 des Diffusors 19 an ausgewählten Umfangspositionen. An ausgewählten zweiten Umfangspositionen des Diffusors 19 verfügen die jeweiligen statorseitigen Leitschaufeln 20 über abweichende Staffelungswinkel.This corresponds to a change in the stagger angle of the stator-
Diejenigen ausgewählten Leitschaufeln 20, die im Vergleich zu den übrigen statorseitigen Leitschaufeln 20 einen unterschiedlichen Staffelungswinkel aufweisen, sind dadurch gekennzeichnet, dass deren Staffelungswinkel insbesondere um ±10°, besonders bevorzugt um ±5°, von den Staffelungswinkeln der übrigen Leitschaufeln 20 des Diffusors 19 abweicht.Those selected
Durch die obigen Maßnahmen der hier vorliegenden Erfindung kann an definierten Umfangspositionen in ungleichmäßigen Umfangsabständen eine etwas höhere oder eine etwas geringere Belastung aus die Leitschaufeln 20 des Diffusors 19 aufgeprägt werden. Die Gefahr instationärer Strömungsphänomene, die zu einer asynchronen Anregung der offenen Laufrädern führen können, kann so reduziert werden.By the above measures of the present invention, a slightly higher or a slightly lower load from the
Nach einem weiteren Aspekt (siehe
Nach diesem weiteren Aspekt weist jedoch mindestens eine statorseitige Leitschaufel 20 des Diffusors 19 zwischen der Strömungseintrittskante 22 und der Strömungsaustrittskante 23 eine abweichende Krümmung auf, nämlich eine Saugseite 24' und eine Druckseite 25' mit gegenüber den anderen Leitschaufeln 20 abweichender Krümmung. Dies ist in
Nach diesem weiteren Aspekt ist es in einem ersten Extremfall möglich, dass ausschließlich eine einzige statorseitige Leitschaufel 20 des Diffusors 19 eine abweichende Krümmung aufweist, dass hingegen alle anderen statorseitigen Leitschaufeln 20 des Diffusors 19 identische Krümmungen aufweisen.According to this further aspect, it is possible in a first extreme that only one
Ebenso ist es nach diesem weiteren Aspekt in einem zweiten Extremfall möglich, dass an alle statorseitige Leitschaufel 20 des Diffusors 19 voneinander abweichende Krümmungen aufweisen.Likewise, according to this further aspect, in a second extreme case, it is possible for all the stator-
Weitere Merkmale der hier vorliegenden Erfindung werden nachfolgend unter Bezugnahme auf
Nach der Erfindung wird zur Reduzierung der Gefahr instationärer Strömungsphänomene, die zu einer asynchronen Anregung der offenen Laufrädern führen können, vorgeschlagen, an mindestens einer dritten Umfangsposition des Diffusorströmungskanals 21 einen zwischen benachbarten statorseitigen Leitschaufeln 20 des Diffusors 19 ausgebildeten Diffusorströmungskanalabschnitt 33 derart zu verändern, dass derselbe gegenüber den an vierten Umfangspositionen ausgebildeten Diffusorströmungskanalabschnitten einen abweichenden Strömungsquerschnitt aufweist.According to the invention, in order to reduce the risk of unsteady flow phenomena that may lead to asynchronous excitation of the open impellers, it is proposed to change at least a third circumferential position of the diffuser flow channel 21 a diffuser flow channel section 33 formed between
So kann
Es ist in einem ersten Extremfall möglich, dass ausschließlich an einer einzigen Umfangspositionen des Diffusorströmungskanals 21 der entsprechende Diffusorströmungskanalabschnitt 33 einen abweichenden Strömungsquerschnitt aufweist, dass hingegen aller anderen Diffusorströmungskanalabschnitte 33 identische Strömungsquerschnitte aufweisen.It is possible in a first extreme case that only at a single circumferential position of the diffuser flow channel 21, the corresponding diffuser flow channel section 33 has a different flow cross-section, however, that all other diffuser flow channel sections 33 have identical flow cross-sections.
Ebenso ist es in einem zweiten Extremfall möglich, dass an allen Umfangspositionen des Diffusorströmungskanals 21 die Diffusorströmungskanalabschnitte 33 jeweils unterschiedliche Strömungsquerschnitte aufweisen.Likewise, in a second extreme case, it is possible for the diffuser flow channel sections 33 to each have different flow cross sections at all circumferential positions of the diffuser flow channel 21.
- 1010
- LaufradWheel
- 1111
- Laufradschaufelimpeller blade
- 1212
- Statorstator
- 1313
- LaufradströmungskanalImpeller flow channel
- 1414
- Nabenkonturhub contour
- 1515
- Statorkonturstator contour
- 1616
- StrömungseintrittskanteFlow inlet edge
- 1717
- StrömungsaustrittskanteFlow outlet edge
- 1818
- Außenflächeouter surface
- 1919
- Diffusordiffuser
- 2020
- Leitschaufelvane
- 2121
- DiffusorströmungskanalDiffuser flow channel
- 2222
- StrömungseintrittskanteFlow inlet edge
- 2323
- StrömungsaustrittskanteFlow outlet edge
- 2424
- Saugseitesuction
- 2525
- Druckseitepressure side
- 2626
- ZwischenströmungskanalBetween flow channel
- 2727
- Rückseiteback
- 2828
- Radseitenraumwheel side
- 2929
- Kreiskonturcircular contour
- 3030
- Kreiskonturcircular contour
- 3131
- SeitenwandSide wall
- 3232
- SeitenwandSide wall
- 3333
- DiffusorströmungskanalabschnittDiffuser flow channel section
- 3434
- Spaltgap
Claims (4)
- A radial compressor stage,
with a stator (12),
with an impeller (10) having multiple rotor-side impeller blades (11) rotating relative to the stator (12), and
with a diffuser (19) positioned in flow direction downstream of the impeller (10) with multiple stator-side guide blades (20), wherein each stator-side guide blade (20) has a flow inlet edge (22) and a flow outlet edge (23), and wherein between the flow inlet edge (22) and the flow outlet edge (23) of the respective guide blade (20) a suction side (24) and a pressure side (25) of the same extend,
wherein between the impeller (10) and the stator (12) a wheel side space (28) is formed, characterized in that
all flow inlet edges (22) of the stator-side guide blades (20) lie on a first circle contour (29) namely in such a manner that the flow inlet edges (22) of all stator-side guide blades (20) have an identical distance from the flow inlet edges (22) of the respective adjacent guide blades (20);
all flow outlet edges (23) of the stator-side guide blades (20) lie on a second circle contour (30) namely in such a manner that in at least one first circumferential position the flow outlet edge (23) of the respective stator-side guide blade (20) has a distance to the flow outlet edge (23) of at least one adjacent guide blade (20) other than in second circumferential positions;
in at least one third circumferential position, a diffuser flow duct section (33) formed between adjacent stator-side guide blades (20) has a flow cross section that deviates with respect to the diffuser flow duct sections formed in fourth circumferential positions. - The radial compressor stage according to Claim 1, characterized in that in the second circumferential positions the respective stator-side guide blades (20) all have identical, second stagger angles; and in the or each first circumferential positions, the respective stator-side guide blades (20) have a first stagger angle that deviates from the second stagger angle.
- The radial compressor stage according to Claim 2, characterized in that the first stagger angle deviates from the second stagger angle by ± 10°, preferably by ±7°, particularly preferably by ± 5°.
- The radial compressor stage according to any one of the Claims 1 to 3, characterized in that compared with the fourth circumferential positions in the or each third circumferential position between the adjacent stator-side guide blades (20) at least one side wall (31, 32) delimiting the diffuser flow duct section (33) is curved towards the inside into the diffuser flow duct section (23) reducing the flow cross section and/or curved towards the outside into the stator (12) enlarging the flow cross section.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014012765.6A DE102014012765A1 (en) | 2014-09-02 | 2014-09-02 | Radial compressor stage |
Publications (3)
Publication Number | Publication Date |
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EP2993357A2 EP2993357A2 (en) | 2016-03-09 |
EP2993357A3 EP2993357A3 (en) | 2016-04-13 |
EP2993357B1 true EP2993357B1 (en) | 2018-02-21 |
Family
ID=53765155
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP15179255.3A Active EP2993357B1 (en) | 2014-09-02 | 2015-07-31 | Radial compressor stage |
Country Status (7)
Country | Link |
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US (1) | US20160061219A1 (en) |
EP (1) | EP2993357B1 (en) |
JP (1) | JP6716220B2 (en) |
CN (1) | CN105387002B (en) |
DE (1) | DE102014012765A1 (en) |
NO (1) | NO3191511T3 (en) |
RU (1) | RU2691699C2 (en) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015219556A1 (en) | 2015-10-08 | 2017-04-13 | Rolls-Royce Deutschland Ltd & Co Kg | Diffuser for radial compressor, centrifugal compressor and turbo machine with centrifugal compressor |
KR102427392B1 (en) * | 2018-01-24 | 2022-07-29 | 한화에어로스페이스 주식회사 | Diffuser for compressor |
EP3650709A1 (en) * | 2018-11-08 | 2020-05-13 | ABB Turbo Systems AG | Bladed diffuser assembly for a radial compressor |
US11098730B2 (en) | 2019-04-12 | 2021-08-24 | Rolls-Royce Corporation | Deswirler assembly for a centrifugal compressor |
EP3848590A1 (en) * | 2020-01-07 | 2021-07-14 | ABB Schweiz AG | Discharge section of a compressor, compressor comprising such a discharge section and turbocharger comprising said compressor |
US11441516B2 (en) | 2020-07-14 | 2022-09-13 | Rolls-Royce North American Technologies Inc. | Centrifugal compressor assembly for a gas turbine engine with deswirler having sealing features |
US11286952B2 (en) | 2020-07-14 | 2022-03-29 | Rolls-Royce Corporation | Diffusion system configured for use with centrifugal compressor |
US11578654B2 (en) | 2020-07-29 | 2023-02-14 | Rolls-Royce North American Technologies Inc. | Centrifical compressor assembly for a gas turbine engine |
RU2757150C1 (en) * | 2020-11-03 | 2021-10-11 | Акционерное общество "Интер РАО - Электрогенерация" | Axial multi-step compressor with water injection into flow part thereof |
CN113882971B (en) * | 2021-09-15 | 2023-02-03 | 浙江理工大学 | Stator guide vane structure of rocket engine turbopump |
Family Cites Families (23)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3006603A (en) * | 1954-08-25 | 1961-10-31 | Gen Electric | Turbo-machine blade spacing with modulated pitch |
US3289921A (en) * | 1965-10-08 | 1966-12-06 | Caterpillar Tractor Co | Vaneless diffuser |
US3658437A (en) * | 1970-03-27 | 1972-04-25 | Caterpillar Tractor Co | Diffuser including vaneless and vaned sections |
US4877373A (en) * | 1988-02-08 | 1989-10-31 | Dresser-Rand Company | Vaned diffuser with small straightening vanes |
SU1525335A1 (en) * | 1988-03-09 | 1989-11-30 | Университет дружбы народов им.Патриса Лумумбы | Centrifugal compressor vaned diffuser |
US4900225A (en) * | 1989-03-08 | 1990-02-13 | Union Carbide Corporation | Centrifugal compressor having hybrid diffuser and excess area diffusing volute |
US5064344A (en) * | 1989-11-01 | 1991-11-12 | Sundstrand Corporation | Partial throat diffuser |
JP2865834B2 (en) * | 1990-09-05 | 1999-03-08 | 株式会社日立製作所 | Centrifugal compressor |
JP3110205B2 (en) * | 1993-04-28 | 2000-11-20 | 株式会社日立製作所 | Centrifugal compressor and diffuser with blades |
DE19502808C2 (en) | 1995-01-30 | 1997-02-27 | Man B & W Diesel Ag | Radial flow machine |
JPH10176699A (en) * | 1996-12-18 | 1998-06-30 | Ishikawajima Harima Heavy Ind Co Ltd | Centrifugal compressor |
DE59809867D1 (en) * | 1998-05-25 | 2003-11-13 | Abb Turbo Systems Ag Baden | centrifugal compressors |
JP2004100553A (en) * | 2002-09-09 | 2004-04-02 | Mitsubishi Heavy Ind Ltd | Stationary blade structure of rotary machine |
US8016557B2 (en) * | 2005-08-09 | 2011-09-13 | Praxair Technology, Inc. | Airfoil diffuser for a centrifugal compressor |
EP1860325A1 (en) * | 2006-05-26 | 2007-11-28 | ABB Turbo Systems AG | Diffuser |
DE102007019264A1 (en) | 2007-04-24 | 2008-11-06 | Man Turbo Ag | filter means |
EP2014925A1 (en) | 2007-07-12 | 2009-01-14 | ABB Turbo Systems AG | Diffuser for radial compressors |
DE102007034236A1 (en) * | 2007-07-23 | 2009-02-05 | Continental Automotive Gmbh | Centrifugal compressor with a diffuser for use with a turbocharger |
JP2009150308A (en) * | 2007-12-20 | 2009-07-09 | Toyota Motor Corp | Centrifugal compressor |
JP5665535B2 (en) * | 2010-12-28 | 2015-02-04 | 三菱重工業株式会社 | Centrifugal compressor |
RU2493439C1 (en) * | 2012-02-17 | 2013-09-20 | Общество с ограниченной ответственностью Деловой центр "Галактика" | Centrifugal pump |
AU2013261587B2 (en) * | 2012-05-16 | 2015-11-19 | Dyson Technology Limited | A fan |
CN103671270B (en) * | 2013-11-30 | 2016-03-30 | 西安交通大学 | The centrifugal compressor that a kind of diffuser vane can vibrate |
-
2014
- 2014-09-02 DE DE102014012765.6A patent/DE102014012765A1/en not_active Withdrawn
-
2015
- 2015-07-31 EP EP15179255.3A patent/EP2993357B1/en active Active
- 2015-08-31 JP JP2015170238A patent/JP6716220B2/en active Active
- 2015-08-31 RU RU2015137073A patent/RU2691699C2/en active
- 2015-09-01 US US14/842,567 patent/US20160061219A1/en not_active Abandoned
- 2015-09-02 CN CN201510553935.7A patent/CN105387002B/en active Active
-
2016
- 2016-11-14 NO NO16798122A patent/NO3191511T3/no unknown
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
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US20160061219A1 (en) | 2016-03-03 |
DE102014012765A1 (en) | 2016-03-03 |
RU2691699C2 (en) | 2019-06-17 |
NO3191511T3 (en) | 2018-02-17 |
EP2993357A2 (en) | 2016-03-09 |
CN105387002B (en) | 2019-10-25 |
CN105387002A (en) | 2016-03-09 |
JP6716220B2 (en) | 2020-07-01 |
RU2015137073A3 (en) | 2018-10-29 |
RU2015137073A (en) | 2017-03-07 |
JP2016053363A (en) | 2016-04-14 |
EP2993357A3 (en) | 2016-04-13 |
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