EP3084227B1 - Compressor stage - Google Patents

Compressor stage Download PDF

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Publication number
EP3084227B1
EP3084227B1 EP14830948.7A EP14830948A EP3084227B1 EP 3084227 B1 EP3084227 B1 EP 3084227B1 EP 14830948 A EP14830948 A EP 14830948A EP 3084227 B1 EP3084227 B1 EP 3084227B1
Authority
EP
European Patent Office
Prior art keywords
compressor stage
impeller
stator
measuring point
annular gap
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
EP14830948.7A
Other languages
German (de)
French (fr)
Other versions
EP3084227A1 (en
Inventor
Alf-Peter Tiedtke
Matthias Wollnik
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.)
MAN Energy Solutions SE
Original Assignee
MAN Diesel and Turbo SE
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Publication date
Application filed by MAN Diesel and Turbo SE filed Critical MAN Diesel and Turbo SE
Publication of EP3084227A1 publication Critical patent/EP3084227A1/en
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Publication of EP3084227B1 publication Critical patent/EP3084227B1/en
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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
    • 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
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • F04D27/001—Testing thereof; Determination or simulation of flow characteristics; Stall or surge detection, e.g. condition monitoring
    • 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
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/10—Stators
    • F05B2240/14—Casings, housings, nacelles, gondels or the like, protecting or supporting assemblies there within
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/20—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2270/00—Control
    • F05B2270/30—Control parameters, e.g. input parameters
    • F05B2270/301—Pressure
    • F05B2270/3011—Inlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2270/00—Control
    • F05B2270/30—Control parameters, e.g. input parameters
    • F05B2270/301—Pressure
    • F05B2270/3015—Pressure differential
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/30—Control parameters, e.g. input parameters
    • F05D2270/301—Pressure
    • F05D2270/3011—Inlet pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/30—Control parameters, e.g. input parameters
    • F05D2270/301—Pressure
    • F05D2270/3015—Pressure differential pressure

Definitions

  • the invention relates to a compressor stage according to the Oberbergriff of claim 1.
  • stator-side components of a compressor stage include an intake manifold, via which medium to be compressed can be introduced into the compressor stage in the region of the compressor stage.
  • stator-side modules include a stator-side flow channel, via which the medium to be compressed, starting from the intake manifold in the direction of a rotor-side impeller can be conveyed.
  • the rotor-side impeller has a radially inner hub, a radially outer cover plate and between the hub and the cover plate extending, also rotor-side impeller blades. A formed between the rotor-side cover plate and the stator gap is sealed by a seal which is held by a seal carrier.
  • the volume flow of the compressor stage determined by a so-called differential pressure measurement.
  • the plus measuring point typically being in the region of a relatively large flow cross-sectional area and thus in the region of a relatively high static flow pressure and the negative Measuring point in the region of a relatively small flow cross-sectional area and thus a relatively small static flow pressure is arranged. Due to the pressure difference between the plus measuring point and the minus measuring point, a signal can be detected which serves to measure the differential pressure.
  • the present invention has the object to provide a novel compressor stage.
  • This object is achieved by a compressor stage according to claim 1.
  • the negative measuring point is positioned upstream of the impeller outside the stator inflow channel in an annular gap branching off from the inflow channel.
  • the present invention it is proposed for the first time to position the minus measuring point for the differential pressure measurement in an annular gap, ie outside the stator inflow channel upstream of the impeller, wherein the annular gap branches off from the inflow channel.
  • annular gap There is a circumferentially averaged pressure distribution in the annular gap, so that the differential pressure measurement is independent of the specific positioning of the minus measuring point seen in the circumferential direction.
  • the differential pressure measurement in the area of the minus measuring point impairing, inhomogeneous flow influences are eliminated by the arrangement of the minus measuring point in the annular gap.
  • a bore diameter can be chosen freely, since the pressure at the minus measuring point in the region of the annular gap is tapped outside the inflow channel.
  • the annular gap branches off immediately upstream of the impeller from the stator inflow channel radially outward.
  • the annular gap adjacent to the impeller is bounded by a stator-side seal carrier which carries a seal cooperating with the cover disk of the rotor-side impeller.
  • the annular gap is bounded by a stator-side housing or by a stator-side inlet star, which is fastened to the stator-side housing.
  • the annular gap is formed like a chamber, wherein the minus measuring point is positioned in a chamber-like portion of the annular gap.
  • the pressure in the region of the minus measuring point of the differential pressure measurement can be further equalized, whereby the differential pressure measurement can be further improved.
  • the present invention relates to a compressor stage, in particular a compressor stage of a centrifugal compressor.
  • the details according to the invention can, however, also be used at a compressor stage for an axial compressor.
  • Fig. 1 shows a detail of a first compressor stage 10 according to the invention, wherein the in Fig. 1 shown compressor stage 10 is the compressor stage of a centrifugal compressor.
  • the compressor stage 10 has an in Fig. 1 not shown on the stator side intake manifold, via which in the region of the compressor stage 10 to be compressed medium in the compressor stage 10 can be introduced or sucked into the compressor stage 10.
  • a stator-side inflow channel 11 which is bounded radially inwardly by a stator-side seal carrier 12 and radially outside of a stator-side housing 13 in the illustrated embodiment, the medium to be compressed to a rotor-side impeller 14 of the compressor stage 10 can be fed.
  • the rotor-side impeller 14 has a shaft 15 with a radially inner hub 16, a radially outer cover plate 17 and between the hub 16 and the cover plate 17 extending impeller blades 18. From the impeller blades 18 is in Fig. 1 a flow inlet edge 19 and a flow outlet edge 20 are shown.
  • a plus-measuring point for differential pressure measurement of the compressor stage 10 is assigned.
  • the plus measuring point of the differential pressure measurement is accordingly positioned in the region of the intake nozzle in the region of a relatively large flow cross-sectional area and accordingly in the region of a relatively high static flow pressure.
  • a negative measuring point for the differential pressure measurement is positioned upstream of the impeller 14 outside the stator inflow channel 11 in an annular gap 24 branching off from the inflow channel.
  • the annular gap 24 branches in the embodiment shown immediately upstream of the impeller 14 from the stator inflow channel 11 radially outward.
  • the minus measuring point is positioned in the region of a relatively small flow cross-sectional area and therefore in the region of a relatively small flow pressure.
  • annular gap 24 leads from radially outside a bore 25 which opens into the annular gap 24, which can be branched off or tapped via this bore 25 of the annular gap 24 and thus the prevailing at the minus measuring point pressure for the differential pressure measurement.
  • annular gap 24 which extends radially outward over the entire circumferential extension of the inflow channel 11 and branches off from it, sets a circumferentially averaged pressure level, so that therefore the tapped for the differential pressure measurement in the negative measuring point pressure is independent of which circumferential position exactly the bore 25 opens into the annular gap 24.
  • Another advantage of the invention is that a nearly arbitrary bore diameter can be selected for the bore 25. Since the pressure prevailing in the annular gap 24 is largely independent of the flow influences the flow in the inflow channel 11, no compromise between the highest possible reliability against clogging due to contamination and signal quality with the smallest possible influence on the flow in the inflow channel 11 for the bore diameter of the bore 25 to get voted.
  • annular gap 24 is limited on the side facing the impeller 14 on the one hand by the seal carrier 23 and on the other hand by a front portion of the cover plate 17.
  • the annular gap 24 is bounded directly by the stator-side housing 13.
  • FIG. 2 A second embodiment of a compressor stage 10 according to the invention shows Fig. 2 , which will be discussed below only on such details, through which the embodiment of the Fig. 1 from the embodiment of Fig. 2 different. With regard to all other details is for the embodiment of the Fig. 2 to the comments on the embodiment of Fig. 1 Reference is made, wherein in the embodiments of the Fig. 1 and 2 same reference numbers are used for the same components.
  • Fig. 2 differs from the embodiment of Fig. 1 only in that in the embodiment of the Fig. 2
  • a stator-side inlet star 27 with inlet guide vanes 30 is present, which radially outwardly bounds the stator inflow channel 11, wherein the annular gap 24, is positioned in the region of the minus measuring point for the differential pressure measurement on the side facing away from the impeller 14 side of this stator inlet star 27 is limited.
  • FIG. 3 Another embodiment of a radial compressor stage 10 according to the invention shows Fig. 3 , wherein the embodiment of the Fig. 3 from the embodiment of Fig. 2 only differs in that the annular gap 24, which is bounded on the side facing away from the impeller 14 by the inlet star 27, chamber-like or expanded like a chamber, wherein the minus-measuring point is positioned in the region of a chamber-like portion 28 of the annular gap 24.
  • a further equalization of the pressure level can take place, whereby the signal quality at the minus measuring point for the differential pressure measurement can be further improved.
  • the plus measuring point is positioned on a section with the largest possible flow cross section and thus with the greatest possible pressure, preferably in the region of the intake manifold, not shown.
  • the minus-measuring point of the differential pressure measurement is positioned in the region of the smallest possible flow cross-section and thus in the range of the smallest possible pressure, namely according to the invention in an annular gap 24, the upstream of the impeller 14 branches off from the stator inflow channel 11, preferably immediately upstream of the inflow channel 11 radially outward ,
  • the pressure level in the annular gap is circumferentially averaged and therefore not dependent on the circumferential position.
  • a chamber-shaped widening of the annular gap 24, the signal quality at the minus measuring point can be further improved.
  • the pressure for the minus measuring point can be tapped via an opening into the annular gap 24 bore 25 at any circumferential position.
  • the bore 25 extends exclusively through the housing 13 and therefore does not have to bridge or cross any part boundaries. Another advantage of the invention is that due to the positioning of the minus measuring point there is no danger that it clogged by contamination.
  • the compressor stage 10 according to the invention is preferably a radial compressor stage.
  • the invention can also be used in a compressor stage for an axial compressor.

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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 Verdichterstufe nach dem Oberbergriff des Anspruchs 1.The invention relates to a compressor stage according to the Oberbergriff of claim 1.

Aus der Praxis bekannte Verdichterstufen verfügen über statorseitige Baugruppen und rotorseitige Baugruppen. Zu den statorseitigen Baugruppen einer Verdichterstufe zählt ein Ansaugstutzen, über welchen im Bereich der Verdichterstufe zu verdichtendes Medium in die Verdichterstufe einleitbar ist. Ferner zählt zu den statorseitigen Baugruppen ein statorseitiger Strömungskanal, über welchen das zu verdichtende Medium ausgehend vom Ansaugstutzen in Richtung auf ein rotorseitiges Laufrad förderbar ist. Das rotorseitige Laufrad verfügt über eine radial innere Nabe, eine radial äußere Deckscheibe und sich zwischen der Nabe und der Deckscheibe erstreckende, ebenfalls rotorseitige Laufradschaufeln. Ein zwischen der rotorseitigen Deckscheibe und dem Stator ausgebildeter Spalt ist über eine Dichtung abgedichtet, die von einem Dichtungsträger gehalten ist.Compressor stages known from practice have stator-side assemblies and rotor-side assemblies. The stator-side components of a compressor stage include an intake manifold, via which medium to be compressed can be introduced into the compressor stage in the region of the compressor stage. Furthermore, the stator-side modules include a stator-side flow channel, via which the medium to be compressed, starting from the intake manifold in the direction of a rotor-side impeller can be conveyed. The rotor-side impeller has a radially inner hub, a radially outer cover plate and between the hub and the cover plate extending, also rotor-side impeller blades. A formed between the rotor-side cover plate and the stator gap is sealed by a seal which is held by a seal carrier.

Zum optimalen Betrieb einer solchen Verdichterstufe ist es von Bedeutung, den durch eine sogenannte Wirkdruckmessung ermittelten Volumenstrom der Verdichterstufe zu kennen. Hierzu ist es aus der Praxis, zum Beispiel aus der DE 2004 038523 A1 oder der JP H08 121381 A bekannt, zur Wirkdruckmessung an der Verdichterstufe an derselben eine sogenannte Plus-Messstelle und eine sogenannte Minus-Messstelle vorzusehen bzw. auszubilden, wobei die Plus-Messstelle typischerweise im Bereich einer relativ großen Strömungsquerschnittsfläche und demnach im Bereich eines relativ hohen statischen Strömungsdrucks und die Minus-Messstelle im Bereich einer relativ kleinen Strömungsquerschnittsfläche und damit eines relativ kleinen statischen Strömungsdrucks angeordnet ist. Aufgrund des Druckunterschieds zwischen der Plus-Messstelle und der Minus-Messstelle kann ein Signal erfasst werden, welches der Wirkdruckmessung dient.For optimum operation of such a compressor stage, it is important to know the volume flow of the compressor stage determined by a so-called differential pressure measurement. For this it is from the practice, for example from the DE 2004 038523 A1 or the JP H08 121381 A It is known to provide or form a so-called plus measuring point and a so-called minus measuring point for the differential pressure measurement at the compressor stage, the plus measuring point typically being in the region of a relatively large flow cross-sectional area and thus in the region of a relatively high static flow pressure and the negative Measuring point in the region of a relatively small flow cross-sectional area and thus a relatively small static flow pressure is arranged. Due to the pressure difference between the plus measuring point and the minus measuring point, a signal can be detected which serves to measure the differential pressure.

Obwohl es bereits bekannt ist, an Verdichterstufen eine Plus-Messstelle und eine Minus-Messstelle zur Wirkdruckmessung vorzusehen, besteht Bedarf an einer Verdichterstufe, an welcher die Wirkdruckmessung besonders vorteilhaft, insbesondere mit hoher Genauigkeit, erfolgen kann. DE 10 2004 038523 A1 offenbart eine Verdichterstufe nach dem Oberbegriff des Anspruchs 1.Although it is already known to provide at compressor stages a plus measuring point and a minus measuring point for differential pressure measurement, there is a need for a compressor stage, on which the differential pressure measurement can be particularly advantageous, in particular with high accuracy. DE 10 2004 038523 A1 discloses a compressor stage according to the preamble of claim 1.

Hiervon ausgehend liegt der vorliegenden Erfindung die Aufgabe zugrunde, eine neuartige Verdichterstufe zu schaffen. Diese Aufgabe wird durch eine Verdichterstufe nach Anspruch 1 gelöst. Erfindungsgemäß ist die Minus-Messstelle stromaufwärts des Laufrads außerhalb des statorseitigen Zuströmkanals in einem vom Zuströmkanal abzweigenden Ringspalt positioniert.On this basis, the present invention has the object to provide a novel compressor stage. This object is achieved by a compressor stage according to claim 1. According to the invention, the negative measuring point is positioned upstream of the impeller outside the stator inflow channel in an annular gap branching off from the inflow channel.

Mit der hier vorliegenden Erfindung wird erstmals vorgeschlagen, die Minus-Messstelle für die Wirkdruckmessung in einem Ringspalt zu positionieren, also außerhalb des statorseitigen Zuströmkanals stromaufwärts des Laufrads, wobei der Ringspalt vom Zuströmkanal abzweigt. Im Ringspalt herrscht eine umfangsgemittelte Druckverteilung, sodass die Wirkdruckmessung unabhängig von der in Umfangsrichtung gesehen konkreten Positionierung der Minus-Messstelle ist. Die Wirkdruckmessung im Bereich der Minus-Messstelle beeinträchtigenden, inhomogenen Strömungseinflüsse werden durch die Anordnung der Minus-Messstelle im Ringspalt eliminiert. Für eine zum Ringspalt von radial außen führende Bohrung, über die der im Ringspalt herrschende Druck abgegriffen bzw. abgezweigt werden kann, kann ein Bohrungsdurchmesser frei gewählt werden, da der Druck an der Minus-Messstelle im Bereich des Ringspalts außerhalb des Zuströmkanals abgegriffen wird.With the present invention, it is proposed for the first time to position the minus measuring point for the differential pressure measurement in an annular gap, ie outside the stator inflow channel upstream of the impeller, wherein the annular gap branches off from the inflow channel. There is a circumferentially averaged pressure distribution in the annular gap, so that the differential pressure measurement is independent of the specific positioning of the minus measuring point seen in the circumferential direction. The differential pressure measurement in the area of the minus measuring point impairing, inhomogeneous flow influences are eliminated by the arrangement of the minus measuring point in the annular gap. For a bore leading radially outward to the annular gap, via which the pressure prevailing in the annular gap can be tapped or branched off, a bore diameter can be chosen freely, since the pressure at the minus measuring point in the region of the annular gap is tapped outside the inflow channel.

Vorzugsweise zweigt der Ringspalt unmittelbar stromaufwärts des Laufrads vom statorseitigen Zuströmkanal nach radial außen ab. Dies erlaubt eine besonders vorteilhafte Wirkdruckmessung, da unmittelbar stromaufwärts des Laufrads der Druck am geringsten ist und somit relativ zur Plus-Messstelle das größte Druckgefälle für die Wirkdruckmessung genutzt werden kann. Erfindungsgemäß ist der Ringspalt benachbart zum Laufrad von einem statorseitigen Dichtungsträger, der eine mit der Deckscheibe des rotorseitigen Laufrads zusammenwirkende Dichtung trägt, begrenzt. Gegenüberliegend zum Laufrad ist der Ringspalt von einem statorseitigen Gehäuse oder von einem statorseitigen Einlaufstern, der an dem statorseitigen Gehäuse befestigt ist, begrenzt. Diese Ausführung ist konstruktiv einfach und erlaubt eine optimale Positionierung der Minus-Messstelle für die Wirkdruckmessung.Preferably, the annular gap branches off immediately upstream of the impeller from the stator inflow channel radially outward. This allows a particularly advantageous differential pressure measurement, since immediately upstream of the impeller, the pressure is lowest and thus can be used relative to the positive measuring point, the largest pressure drop for differential pressure measurement. According to the invention, the annular gap adjacent to the impeller is bounded by a stator-side seal carrier which carries a seal cooperating with the cover disk of the rotor-side impeller. Opposite the impeller, the annular gap is bounded by a stator-side housing or by a stator-side inlet star, which is fastened to the stator-side housing. This design is structurally simple and allows optimal positioning of the minus measuring point for differential pressure measurement.

Nach einer weiteren vorteilhaften Weiterbildung ist der Ringspalt kammerartig ausgebildet, wobei die Minus-Messstelle in einem kammerartigen Abschnitt des Ringspalts positioniert ist. In dem kammerartigen Abschnitt kann sich der Druck im Bereich der Minus-Messstelle der Wirkdruckmessung weiter vergleichmäßigen, wodurch die Wirkdruckmessung weiter verbessert werden kann.According to a further advantageous development of the annular gap is formed like a chamber, wherein the minus measuring point is positioned in a chamber-like portion of the annular gap. In the chamber-like section, the pressure in the region of the minus measuring point of the differential pressure measurement can be further equalized, whereby the differential pressure measurement can be further improved.

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:
ein Detail einer ersten erfindungsgemäßen Verdichterstufe im Meridionalschnitt;
Fig. 2:
ein Detail einer zweiten erfindungsgemäßen Verdichterstufe im Meridionalschnitt; und
Fig. 3:
ein Detail einer dritten erfindungsgemäßen Verdichterstufe im Meridionalschnitt.
Preferred embodiments of the invention will become apparent from the dependent claims and the description below. Embodiments of the invention will be described, without being limited thereto, with reference to the drawings. Showing:
Fig. 1:
a detail of a first compressor stage according to the invention in meridional section;
Fig. 2:
a detail of a second compressor stage according to the invention in meridional section; and
3:
a detail of a third compressor stage according to the invention in meridional section.

Die hier vorliegende Erfindung betrifft eine Verdichterstufe, insbesondere eine Verdichterstufe eines Radialverdichters. Die erfindungsgemäßen Details können iedoch auch an einer Verdichterstufe für einen Axialverdichter genutzt werden.The present invention relates to a compressor stage, in particular a compressor stage of a centrifugal compressor. The details according to the invention can, however, also be used at a compressor stage for an axial compressor.

Fig. 1 zeigt ein Detail einer ersten erfindungsgemäßen Verdichterstufe 10, wobei es sich bei der in Fig. 1 gezeigten Verdichterstufe 10 um die Verdichterstufe eines Radialverdichters handelt. Fig. 1 shows a detail of a first compressor stage 10 according to the invention, wherein the in Fig. 1 shown compressor stage 10 is the compressor stage of a centrifugal compressor.

Die Verdichterstufe 10 verfügt über einen in Fig. 1 nicht gezeigten statorseitigen Ansaugstutzen, über welchen im Bereich der Verdichterstufe 10 zu verdichtendes Medium in die Verdichterstufe 10 einleitbar bzw. in die Verdichterstufe 10 ansaugbar ist.The compressor stage 10 has an in Fig. 1 not shown on the stator side intake manifold, via which in the region of the compressor stage 10 to be compressed medium in the compressor stage 10 can be introduced or sucked into the compressor stage 10.

Über einen statorseitigen Zuströmkanal 11, der im gezeigten Ausführungsbeispiel radial innen von einem statorseitigen Dichtungsträger 12 und radial außen von einem statorseitigen Gehäuse 13 begrenzt ist, ist das zu verdichtende Medium einem rotorseitigen Laufrad 14 der Verdichterstufe 10 zuführbar.Via a stator-side inflow channel 11, which is bounded radially inwardly by a stator-side seal carrier 12 and radially outside of a stator-side housing 13 in the illustrated embodiment, the medium to be compressed to a rotor-side impeller 14 of the compressor stage 10 can be fed.

Das rotorseitige Laufrad 14 verfügt über eine Welle 15 mit einer radial inneren Nabe 16, eine radial äußere Deckscheibe 17 sowie sich zwischen der Nabe 16 und der Deckscheibe 17 erstreckende Laufradschaufeln 18. Von den Laufradschaufeln 18 ist in Fig. 1 eine Strömungseintrittskante 19 und eine Strömungsaustrittskante 20 gezeigt.The rotor-side impeller 14 has a shaft 15 with a radially inner hub 16, a radially outer cover plate 17 and between the hub 16 and the cover plate 17 extending impeller blades 18. From the impeller blades 18 is in Fig. 1 a flow inlet edge 19 and a flow outlet edge 20 are shown.

Ein Spalt 29, der zwischen der rotorseitigen Welle 15 des Laufrads 14 und dem statorseitigen Dichtungsträger 12 ausgebildet ist, ist über eine von diesem statorseitigen Dichtungsträger 12 getragene Dichtung 20 abgedichtet.A gap 29, which is formed between the rotor-side shaft 15 of the impeller 14 and the stator-side seal carrier 12, is sealed by a seal 20 carried by this stator-side seal carrier 12.

Ein Spalt 21, der zwischen dem statorseitigen Gehäuse 13 und der Deckscheibe 17 des rotorseitigen Laufrads 14 ausgebildet ist, ist von einer Dichtung 22 abgedichtet, die von einem weiteren statorseitigen Dichtungsträger 23 gehalten ist.A gap 21, which is formed between the stator-side housing 13 and the cover plate 17 of the rotor-side impeller 14, is sealed by a seal 22, which is held by a further stator-side seal carrier 23.

Im Bereich des in Fig. 1 nicht gezeigten Ansaugstutzens, über welchen der Verdichterstufe zu verdichtendes Medium zuführbar ist, ist eine Plus-Messstelle zur Wirkdruckmessung der Verdichterstufe 10 zugeordnet. Die Plus-Messstelle der Wirkdruckmessung ist demnach im Bereich des Ansaugstutzens im Bereich einer relativ großen Strömungsquerschnittsfläche und demnach im Bereich eines relativ hohen statischen Strömungsdrucks positioniert.In the area of in Fig. 1 not shown intake, via which the compressor stage to be compressed medium can be fed, a plus-measuring point for differential pressure measurement of the compressor stage 10 is assigned. The plus measuring point of the differential pressure measurement is accordingly positioned in the region of the intake nozzle in the region of a relatively large flow cross-sectional area and accordingly in the region of a relatively high static flow pressure.

Eine Minus-Messstelle für die Wirkdruckmessung ist stromaufwärts des Laufrads 14 außerhalb des statorseitigen Zuströmkanals 11 in einem vom Zuströmkanal abzweigenden Ringspalt 24 positioniert. Der Ringspalt 24 zweigt im gezeigten Ausführungsbeispiel unmittelbar stromaufwärts des Laufrads 14 vom statorseitigen Zuströmkanal 11 nach radial außen ab. Die Minus-Messstelle ist im Bereich einer relativ kleinen Strömungsquerschnittsfläche und demnach im Bereich eines relativ kleinen Strömungsdrucks positioniert.A negative measuring point for the differential pressure measurement is positioned upstream of the impeller 14 outside the stator inflow channel 11 in an annular gap 24 branching off from the inflow channel. The annular gap 24 branches in the embodiment shown immediately upstream of the impeller 14 from the stator inflow channel 11 radially outward. The minus measuring point is positioned in the region of a relatively small flow cross-sectional area and therefore in the region of a relatively small flow pressure.

Zu diesem Ringspalt 24 führt von radial außen eine Bohrung 25, die in den Ringspalt 24 mündet, wobei über diese Bohrung 25 der im Ringspalt 24 und damit der an der Minus-Messstelle herrschende Druck für die Wirkdruckmessung abgezweigt bzw. abgegriffen werden kann.To this annular gap 24 leads from radially outside a bore 25 which opens into the annular gap 24, which can be branched off or tapped via this bore 25 of the annular gap 24 and thus the prevailing at the minus measuring point pressure for the differential pressure measurement.

Im Ringspalt 24, der sich radial außen über die gesamte Umfangserstreckung des Zuströmkanals 11 erstreckt und von diesem abzweigt, stellt sich ein umfangsgemitteltes Druckniveau ein, sodass demnach der für die Wirkdruckmessung im Bereich der Minus-Messstelle abgreifbare Druck unabhängig davon ist, an welcher Umfangsposition genau die Bohrung 25 in den Ringspalt 24 mündet.In the annular gap 24, which extends radially outward over the entire circumferential extension of the inflow channel 11 and branches off from it, sets a circumferentially averaged pressure level, so that therefore the tapped for the differential pressure measurement in the negative measuring point pressure is independent of which circumferential position exactly the bore 25 opens into the annular gap 24.

Ferner können hierdurch inhomogene Strömungseinflüsse auf den im Bereich der Minus-Messstelle herrschenden Druck weitestgehend minimiert werden.Furthermore, as a result, inhomogeneous flow influences on the pressure prevailing in the area of the minus measuring point can be minimized as far as possible.

Ein weiterer Vorteil der Erfindung liegt darin, dass für die Bohrung 25 ein nahezu beliebiger Bohrungsdurchmesser gewählt werden kann. Da der im Ringspalt 24 herrschende Druck weitestgehend unabhängig von den Strömungseinflüssen der Strömung im Zuströmkanal 11 ist, muss für den Bohrungsdurchmesser der Bohrung 25 kein Kompromiss zwischen einer möglichst hohen Betriebssicherheit gegen Zusetzen durch Verschmutzung und Signalqualität mit einem möglichst geringen Einfluss auf die Strömung im Zuströmkanal 11 gewählt werden.Another advantage of the invention is that a nearly arbitrary bore diameter can be selected for the bore 25. Since the pressure prevailing in the annular gap 24 is largely independent of the flow influences the flow in the inflow channel 11, no compromise between the highest possible reliability against clogging due to contamination and signal quality with the smallest possible influence on the flow in the inflow channel 11 for the bore diameter of the bore 25 to get voted.

Im Ausführungsbeispiel der Fig. 1 ist der Ringspalt 24 auf der dem Laufrad 14 zugewandten Seite einerseits vom Dichtungsträger 23 und andererseits von einem vorderen Abschnitt der Deckscheibe 17 begrenzt. Auf der dem Laufrad 14 gegenüberliegenden Seite ist in Fig. 1 der Ringspalt 24 unmittelbar vom statorseitigen Gehäuse 13 begrenzt.In the embodiment of Fig. 1 the annular gap 24 is limited on the side facing the impeller 14 on the one hand by the seal carrier 23 and on the other hand by a front portion of the cover plate 17. On the opposite side of the impeller 14 is in Fig. 1 the annular gap 24 is bounded directly by the stator-side housing 13.

Ein zweites Ausführungsbeispiel einer erfindungsgemäßen Verdichterstufe 10 zeigt Fig. 2, wobei nachfolgend nur auf solche Details eingegangen wird, durch die sich das Ausführungsbeispiel der Fig. 1 vom Ausführungsbeispiel der Fig. 2 unterscheidet. Hinsichtlich aller übrigen Details wird für das Ausführungsbeispiel der Fig. 2 auf die Ausführungen zum Ausführungsbeispiel der Fig. 1 Bezug genommen, wobei in den Ausführungsbeispielen der Fig. 1 und 2 für gleiche Baugruppen gleiche Bezugsziffern verwendet werden.A second embodiment of a compressor stage 10 according to the invention shows Fig. 2 , which will be discussed below only on such details, through which the embodiment of the Fig. 1 from the embodiment of Fig. 2 different. With regard to all other details is for the embodiment of the Fig. 2 to the comments on the embodiment of Fig. 1 Reference is made, wherein in the embodiments of the Fig. 1 and 2 same reference numbers are used for the same components.

Das Ausführungsbeispiel der Fig. 2 unterscheidet sich vom Ausführungsbeispiel der Fig. 1 lediglich dadurch, dass im Ausführungsbeispiel der Fig. 2 zusätzlich ein statorseitiger Einlaufstern 27 mit Eintrittsleitschaufeln 30 vorhanden ist, welcher den statorseitigen Zuströmkanal 11 radial außen abschnittsweise begrenzt, wobei der Ringspalt 24, im Bereich dessen die Minus-Messstelle für die Wirkdruckmessung positioniert ist, auf der vom Laufrad 14 abgewandten Seite von diesem statorseitigen Einlaufstern 27 begrenzt ist.The embodiment of Fig. 2 differs from the embodiment of Fig. 1 only in that in the embodiment of the Fig. 2 In addition, a stator-side inlet star 27 with inlet guide vanes 30 is present, which radially outwardly bounds the stator inflow channel 11, wherein the annular gap 24, is positioned in the region of the minus measuring point for the differential pressure measurement on the side facing away from the impeller 14 side of this stator inlet star 27 is limited.

Ein weiteres Ausführungsbeispiel einer erfindungsgemäßen Radialverdichterstufe 10 zeigt Fig. 3, wobei sich das Ausführungsbeispiel der Fig. 3 vom Ausführungsbeispiel der Fig. 2 lediglich dadurch unterscheidet, dass der Ringspalt 24, welcher an der vom Laufrad 14 abgewandten Seite durch den Einlaufstern 27 begrenzt ist, kammerartig ausgebildet bzw. kammerartig aufgeweitet ist, wobei die Minus-Messstelle im Bereich eines kammerartigen Abschnitts 28 des Ringspalts 24 positioniert ist. In diesem kammerartigen Abschnitt 28 kann eine weitere Vergleichmäßigung des Druckniveaus erfolgen, wodurch die Signalqualität an der Minus-Messstelle für die Wirkdruckmessung weiter verbessert werden kann.Another embodiment of a radial compressor stage 10 according to the invention shows Fig. 3 , wherein the embodiment of the Fig. 3 from the embodiment of Fig. 2 only differs in that the annular gap 24, which is bounded on the side facing away from the impeller 14 by the inlet star 27, chamber-like or expanded like a chamber, wherein the minus-measuring point is positioned in the region of a chamber-like portion 28 of the annular gap 24. In this chamber-like section 28, a further equalization of the pressure level can take place, whereby the signal quality at the minus measuring point for the differential pressure measurement can be further improved.

Bei der Verdichterstufe 10 ist demnach die Plus-Messstelle an einem Abschnitt mit einem möglichst großen Strömungsquerschnitt und damit mit einem möglichst großen Druck positioniert, vorzugsweise im Bereich des nicht gezeigten Ansaugstutzens. Die Minus-Messstelle der Wirkdruckmessung ist im Bereich eines möglichst kleinen Strömungsquerschnitts und damit im Bereich eines möglichst kleinen Drucks positioniert, nämlich erfindungsgemäß in einem Ringspalt 24, der stromaufwärts des Laufrads 14 vom statorseitigen Zuströmkanal 11 abzweigt, vorzugsweise unmittelbar stromaufwärts des Zuströmkanals 11 nach radial außen. Das Druckniveau im Ringspalt ist umfangsgemittelt und demnach nicht von der Umfangsposition abhängig. Über eine kammerförmige Aufweitung des Ringspalts 24 kann die Signalqualität an der Minus-Messstelle weiter verbessert werden. Der Druck für die Minus-Messstelle kann über eine in den Ringspalt 24 mündende Bohrung 25 an einer beliebigen Umfangsposition abgegriffen werden. Die Bohrung 25 erstreckt sich dabei ausschließlich durch das Gehäuse 13 und muss demnach keine Bauteilgrenzen überbrücken bzw. überqueren. Ein weiterer Vorteil der Erfindung besteht darin, dass infolge der Positionierung der Minus-Messstelle keine Gefahr besteht, dass dieselbe durch eine Verschmutzung verstopft.In the compressor stage 10, therefore, the plus measuring point is positioned on a section with the largest possible flow cross section and thus with the greatest possible pressure, preferably in the region of the intake manifold, not shown. The minus-measuring point of the differential pressure measurement is positioned in the region of the smallest possible flow cross-section and thus in the range of the smallest possible pressure, namely according to the invention in an annular gap 24, the upstream of the impeller 14 branches off from the stator inflow channel 11, preferably immediately upstream of the inflow channel 11 radially outward , The pressure level in the annular gap is circumferentially averaged and therefore not dependent on the circumferential position. A chamber-shaped widening of the annular gap 24, the signal quality at the minus measuring point can be further improved. The pressure for the minus measuring point can be tapped via an opening into the annular gap 24 bore 25 at any circumferential position. The bore 25 extends exclusively through the housing 13 and therefore does not have to bridge or cross any part boundaries. Another advantage of the invention is that due to the positioning of the minus measuring point there is no danger that it clogged by contamination.

Bei der erfindungsgemäßen Verdichterstufe 10 handelt es sich vorzugsweise um eine Radialverdichterstufe. Die Erfindung kann jedoch auch bei einer Verdichterstufe für einen Axialverdichter Verwendung finden.The compressor stage 10 according to the invention is preferably a radial compressor stage. However, the invention can also be used in a compressor stage for an axial compressor.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

1010
Verdichterstufecompressor stage
1111
Zuströmkanalinflow
1212
Dichtungsträgerseal carrier
1313
Gehäusecasing
1414
LaufradWheel
1515
Wellewave
1616
Nabehub
1717
Deckscheibecover disc
1818
Laufradschaufelimpeller blade
1919
StrömungseintrittskanteFlow inlet edge
2020
StrömungsaustrittskanteFlow outlet edge
2121
Spaltgap
2222
Dichtungpoetry
2323
Dichtungsträgerseal carrier
2424
Ringspaltannular gap
2525
Bohrungdrilling
2626
Dichtungpoetry
2727
Einlaufsternfeed star
2828
Kammerchamber
2929
Spaltgap
3030
Eintrittsleitschaufelinlet guide vane

Claims (8)

  1. A compressor stage, with a stator-side intake connector, via which during the operation of the compressor stage medium to be compressed in the region of the compressor stage can be fed into the compressor stage, with a stator-side inflow passage (11), via which the medium to be compressed emanating from the intake connector can be conveyed in the direction of a rotor-side impeller (14), wherein the impeller (14) comprises a radially inner hub (16) and impeller blades (18), wherein for the effective pressure measurement on the compressor stage a plus measuring point and a minus measuring point are provided on the same, wherein the minus measuring point is positioned upstream of the impeller (14) outside the stator-side inflow passage (11) in an annular gap (24) branching off the inflow passage (11), characterized in that the impeller (14) comprises a radially outer shroud (17), wherein the impeller blades (18) extend between the hub (16) and the shroud (17), and in that the annular gap (24) is delimited adjacent to the impeller (14) by a stator-side seal carrier (23), which carries a seal (22) that interacts with the shroud (17) of the rotor-side impeller (17).
  2. The compressor stage according to Claim 1, characterized in that the annular gap (24) directly upstream of the impeller (14) branches off the stator-side inflow passage (11) to radially outside.
  3. The compressor stage according to Claim 1, characterized in that the annular gap (24) located opposite the impeller (14) is delimited by a stator-side housing (13).
  4. The compressor stage according to Claim 1, characterized in that the annular gap (24) located opposite the impeller (14) is delimited by a stator-side inlet star (27) which is attached to a stator-side housing (13).
  5. The compressor stage according to any one of the Claims 1 to 4, characterized in that the annular gap (24) is formed chamber-like, wherein the minus measuring point is positioned in a chamber-like section (28) of the annular gap (24).
  6. The compressor stage according to any one of the Claims 1 to 5, characterized in that from radially outside a bore (25) leads to the minus measuring point, via which the pressure level present at the minus measuring point can be picked off.
  7. The compressor stage according to any one of the Claims 1 to 6, characterized in that the plus measuring point is positioned in the region of the intake connector.
  8. The compressor stage according to any one of the Claims 1 to 7, characterized in that the same is a radial compressor stage.
EP14830948.7A 2013-12-17 2014-12-16 Compressor stage Not-in-force EP3084227B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102013020825 2013-12-17
DE102014001998.5A DE102014001998A1 (en) 2013-12-17 2014-02-17 compressor stage
PCT/EP2014/003377 WO2015090566A1 (en) 2013-12-17 2014-12-16 Compressor stage

Publications (2)

Publication Number Publication Date
EP3084227A1 EP3084227A1 (en) 2016-10-26
EP3084227B1 true EP3084227B1 (en) 2018-10-31

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Application Number Title Priority Date Filing Date
EP14830948.7A Not-in-force EP3084227B1 (en) 2013-12-17 2014-12-16 Compressor stage

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US (1) US10519975B2 (en)
EP (1) EP3084227B1 (en)
CN (1) CN105814317B (en)
DE (1) DE102014001998A1 (en)
RU (1) RU2634648C1 (en)
WO (1) WO2015090566A1 (en)

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RU2692173C1 (en) * 2018-02-15 2019-06-21 Акционерное общество "Научно-производственная фирма "Невинтермаш" Centrifugal stage
RU2697244C1 (en) * 2018-10-24 2019-08-13 Владимир Иванович Савичев Bladeless radial centrifugal compressor

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Publication number Priority date Publication date Assignee Title
SU1514978A1 (en) * 1987-07-15 1989-10-15 Научно-производственное объединение по сельскохозяйственному машиностроению Radial fan casing
DE3909180A1 (en) * 1989-03-21 1990-09-27 Hv Turbo A S Device for determining mass flow
DE4416497C1 (en) * 1994-05-10 1995-01-12 Gutehoffnungshuette Man Geared multi-shaft turbo-compressor and geared multi-shaft radial expander
JPH08121381A (en) * 1994-10-20 1996-05-14 Hitachi Ltd Ventilating device for vehicle
DE102004038523A1 (en) 2004-08-07 2006-03-16 Audi Ag Turbocharger compressor has air volume sensing device in compressor inlet with at least one air pressure measuring point connected to air inlet by air tapping
ITBO20040742A1 (en) * 2004-11-30 2005-02-28 Spal Srl CENTRIFUGAL FAN
CN202182742U (en) * 2011-08-02 2012-04-04 威海文润测控设备有限公司 High-precision cone pressure-taking flowmeter
CN102759427A (en) * 2012-07-13 2012-10-31 西安交通大学 Visualized pressure measuring device for porous media filling structure
CN203069318U (en) * 2013-02-04 2013-07-17 扬州大学 Uniform-pressure sleeve for static pressure measurement of pipe cross section
JP6146469B2 (en) * 2013-07-05 2017-06-14 株式会社Ihi Turbo compressor flow measuring device and turbo compressor
CN103759884B (en) * 2014-01-29 2016-03-02 中国商用飞机有限责任公司 Device and method for measuring static pressure of high-speed fluid in high-pressure pipeline

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Publication number Publication date
US10519975B2 (en) 2019-12-31
US20160319838A1 (en) 2016-11-03
CN105814317B (en) 2018-10-12
EP3084227A1 (en) 2016-10-26
DE102014001998A1 (en) 2015-06-18
RU2634648C1 (en) 2017-11-02
CN105814317A (en) 2016-07-27
WO2015090566A1 (en) 2015-06-25

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