EP3084227A1 - Compressor stage - Google Patents

Compressor stage

Info

Publication number
EP3084227A1
EP3084227A1 EP14830948.7A EP14830948A EP3084227A1 EP 3084227 A1 EP3084227 A1 EP 3084227A1 EP 14830948 A EP14830948 A EP 14830948A EP 3084227 A1 EP3084227 A1 EP 3084227A1
Authority
EP
European Patent Office
Prior art keywords
compressor stage
impeller
stator
annular gap
measuring point
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP14830948.7A
Other languages
German (de)
French (fr)
Other versions
EP3084227B1 (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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by MAN Diesel and Turbo SE filed Critical MAN Diesel and Turbo SE
Publication of EP3084227A1 publication Critical patent/EP3084227A1/en
Application granted granted Critical
Publication of EP3084227B1 publication Critical patent/EP3084227B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • 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 assemblies and rotor-side assemblies.
  • stator-side modules To the stator-side modules of a
  • Compressor stage counts an intake, above which in the field of
  • 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 see 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 present invention has the object to provide a novel compressor stage. This task is accomplished by a
  • Inflow channel positioned in a branching off from the inflow channel annular gap.
  • 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 circumferential pressure distribution in the annular gap, so that the differential pressure measurement is independent of the specific positioning of the minus measuring point in the circumferential direction.
  • the differential pressure measurement in the area of the negative measuring point affecting 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 outside the inflow channel is tapped ,
  • 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.
  • the annular gap adjacent to the impeller of a stator-side seal carrier which carries a cooperating with the cover plate of the rotor-side impeller seal limited.
  • 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.
  • 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.
  • FIG. 1 shows a detail of a first compressor stage according to the invention in FIG
  • FIG. 2 shows a detail of a second compressor stage according to the invention in FIG.
  • FIG. 3 shows a detail of a third compressor stage according to the invention in FIG.
  • the present invention relates to a compressor stage, in particular a compressor stage of a centrifugal compressor.
  • a compressor stage in particular a compressor stage of a centrifugal compressor.
  • the details according to the invention can also be used at a compressor stage for an axial compressor.
  • 1 shows a detail of a first compressor stage 10 according to the invention, the compressor stage 10 shown in FIG. 1 being the compressor stage of a radial compressor.
  • the compressor stage 10 has a stator-side intake manifold, not shown in FIG. 1, via which medium to be compressed can be introduced into the compressor stage 10 or can be sucked into the compressor stage 10 in the region of 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 is shown.
  • a plus-measuring point for measuring the effective pressure 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
  • stator-side 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.
  • a circumferentially-mediated pressure level sets in, so that the pressure which can be tapped for the differential pressure measurement in the region of the minus measuring point is independent of which Circumferential position exactly the bore 25 opens into the annular gap 24.
  • the annular gap 24 is bounded 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 disk 17. On the side opposite the impeller 14, the annular gap 24 in FIG. 1 is limited directly by the stator-side housing 13.
  • FIG. 2 A second embodiment of a compressor stage 10 according to the invention is shown in FIG. 2, wherein only those details are discussed below, by which the embodiment of FIG. 1 differs from the embodiment of FIG. With regard to all the other details, reference is made to the embodiments of the embodiment of FIG. 1 for the embodiment of FIG. 2, wherein in the exemplary embodiments of FIGS. 1 and 2 the 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 FIG. 2 in addition a stator inlet star 27 with inlet guide vanes 30 is present, which limits the stator inflow channel 11 radially outwardly in sections, wherein the annular gap 24, in the area of which the minus measuring point is positioned for the differential pressure measurement, on the side facing away from the impeller 14 of this stator inlet star 27 is limited.
  • the embodiment of FIG. 3 differs from the embodiment of FIG. 2 only 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 chamber-like widened, wherein the minus measuring point is positioned in the region of a chamber-like portion 28 of the annular gap 24.
  • this chamber-like portion 28 may be another
  • 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 a smallest possible flow cross-section and thus in the region of the smallest possible pressure, namely according to the invention in an annular gap 24 which branches off from the stator-side inflow channel 11 upstream of the impeller 14, preferably immediately upstream of the inflow channel 11 radially outside.
  • 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 in a
  • Compressor stage for an axial compressor find use. LIST OF REFERENCE NUMBERS

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

A compressor stage (10), having a stator-side intake connector via which medium for compression in the region of the compressor stage can be introduced into the compressor stage, having a stator-side inflow duct (11) via which the medium for compression can be conveyed from the intake connector in the direction of a rotor-side impeller (14), wherein the impeller (14) has a radially inner hub (16), a radially outer cover disk (17) and impeller blades (18) which extend between the hub (16) and the cover disk (17), wherein for measurement of the effective pressure at the compressor stage, there is provided at the latter a plus measurement point and a minus measurement point, wherein the minus measurement point is positioned upstream of the impeller (14), outside the stator-side inflow duct (11), in an annular gap (24) which branches off from the inflow duct (11).

Description

Verdichterstufe  compressor stage
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 Compressor stages known from practice have stator-side assemblies and rotor-side assemblies. To the stator-side modules of a
Verdichterstufe zählt ein Ansaugstutzen, über welchen im Bereich der Compressor stage counts an intake, above which in the field of
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 zwi- sehen 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 to be compressed medium in the compressor stage can be introduced. 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 see 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 For optimal operation of such a compressor stage, it is important to determine the volume flow rate determined by a so-called differential pressure measurement
Verdichterstufe zu kennen. Hierzu ist es aus der Praxis 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 To know the compressor stage. For this purpose, it is known from practice to provide or form a so-called plus measuring point and a so-called minus measuring point for differential pressure measurement at the compressor stage on the same, the plus measuring point typically in the range of a relatively large
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 Flow cross-sectional area and therefore in the range of a relatively high static flow pressure and the minus 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 is the
\A/irLrH ri i^moc i inn Hiont 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, insbe- sondere mit hoher Genauigkeit, erfolgen kann. Hiont Although it is already known to provide a plus measuring point and a minus measuring point for differential pressure measurement at compressor stages, there is a need for a compressor stage on which the differential pressure measurement can be carried out particularly advantageously, in particular with high accuracy.
Hiervon ausgehend liegt der vorliegenden Erfindung die Aufgabe zugrunde, eine neuartige Verdichterstufe zu schaffen. Diese Aufgabe wird durch eine On this basis, the present invention has the object to provide a novel compressor stage. This task is accomplished by a
Verdichterstufe nach Anspruch 1 gelöst. Erfindungsgemäß ist die Minus- Messstelle stromaufwärts des Laufrads außerhalb des statorseitigen Compressor stage solved according to claim 1. According to the invention, the minus measuring point upstream of the impeller is outside the stator
Zuströmkanals in einem vom Zuströmkanal abzweigenden Ringspalt positioniert.  Inflow channel positioned in a branching off from the inflow channel annular gap.
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 umfangs- gemittelte Druckverteilung, sodass die Wirkdruckmessung unabhängig von der in Umfangsrichtung gesehen konkreten Positionierung der Minus-Messstelle ist. Die Wirkdruckmessung im Bereich der Minus-Messstelle beeinträchtigenden, inhomo- genen 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 abge- griffen 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 circumferential pressure distribution in the annular gap, so that the differential pressure measurement is independent of the specific positioning of the minus measuring point in the circumferential direction. The differential pressure measurement in the area of the negative measuring point affecting inhomogeneous flow influences are eliminated by the arrangement of the minus measuring point in the annular gap. For a bore leading radially outwards 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 outside the inflow channel is tapped ,
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. Nach einer vorteilhaften Weiterbildung ist der Ringspalt benachbart zum Laufrad von einem statorseitigen Dichtungsträger, der eine mit der Deckscheibe des rotor- seitigen 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 an advantageous development of the annular gap adjacent to the impeller of a stator-side seal carrier, which carries a cooperating with the cover plate of the rotor-side impeller seal limited. 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: 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 : ein Detail einer ersten erfindungsgemäßen Verdichterstufe im 1 shows a detail of a first compressor stage according to the invention in FIG
Meridionalschnitt;  meridional;
Fig. 2: ein Detail einer zweiten erfindungsgemäßen Verdichterstufe im  FIG. 2 shows a detail of a second compressor stage according to the invention in FIG
Meridionalschnitt; und  meridional; and
Fig. 3: ein Detail einer dritten erfindungsgemäßen Verdichterstufe im 3 shows a detail of a third compressor stage according to the invention in FIG
Meridionalschnitt.  Meridional.
Die hier vorliegende Erfindung betrifft eine Verdichterstufe, insbesondere eine Verdichterstufe eines Radialverdichters. Die erfindungsgemäßen Details können iedoch auch an einer Verdichterstufe für einen Axialverdichter aenutzt werden. 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. The present invention relates to a compressor stage, in particular a compressor stage of a centrifugal compressor. However, the details according to the invention can also be used at a compressor stage for an axial compressor. 1 shows a detail of a first compressor stage 10 according to the invention, the compressor stage 10 shown in FIG. 1 being the compressor stage of a radial 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 a stator-side intake manifold, not shown in FIG. 1, via which medium to be compressed can be introduced into the compressor stage 10 or can be sucked into the compressor stage 10 in the region of 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 is 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. 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. 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. In the region of the intake manifold, not shown in Fig. 1, via which the compressor stage is to be compressed medium fed, a plus-measuring point for measuring the effective pressure 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 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
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. stator-side 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 umfangsge- mitteltes 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, a circumferentially-mediated pressure level sets in, so that the pressure which can be tapped for the differential pressure measurement in the region of the minus measuring point 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. 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 1 ist, muss für den Bohrungsdurchmesser der Boh- rung 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. 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. 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 of the flow in the inflow channel 1, no compromise has to be made between the highest possible operational reliability against clogging by pollution and signal quality with the least possible influence on the flow in the bore Inflow channel 11 can be selected.
Im Ausführungsbeispiel der Fig. 1 ist der Ringspalt 24 auf der dem Laufrad 14 zu- gewandten 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 exemplary embodiment of FIG. 1, the annular gap 24 is bounded 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 disk 17. On the side opposite the impeller 14, the annular gap 24 in FIG. 1 is limited 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 genom- men, 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 is shown in FIG. 2, wherein only those details are discussed below, by which the embodiment of FIG. 1 differs from the embodiment of FIG. With regard to all the other details, reference is made to the embodiments of the embodiment of FIG. 1 for the embodiment of FIG. 2, wherein in the exemplary embodiments of FIGS. 1 and 2 the 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. 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 2 differs from the embodiment of FIG. 1 only in that in the embodiment of FIG. 2 in addition a stator inlet star 27 with inlet guide vanes 30 is present, which limits the stator inflow channel 11 radially outwardly in sections, wherein the annular gap 24, in the area of which the minus measuring point is positioned for the differential pressure measurement, on the side facing away from the impeller 14 of this stator inlet star 27 is limited. 3, wherein the embodiment of FIG. 3 differs from the embodiment of FIG. 2 only 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 chamber-like widened, 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 portion 28 may be another
Vergleichmäßigung des Druckniveaus erfolgen, wodurch die Signalqualität an der Minus-Messstelle für die Wirkdruckmessung weiter verbessert werden kann. Uniformity of the pressure level, 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 mög- liehst 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 Um- fangsposition 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 a smallest possible flow cross-section and thus in the region of the smallest possible pressure, namely according to the invention in an annular gap 24 which branches off from the stator-side inflow channel 11 upstream of the impeller 14, preferably immediately upstream of the inflow channel 11 radially outside. 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 The compressor stage 10 according to the invention is preferably a radial compressor stage. However, the invention can also in a
Verdichterstufe für einen Axialverdichter Verwendung finden. Bezugszeichenliste Compressor stage for an axial compressor find use. LIST OF REFERENCE NUMBERS
10 Verdichterstufe 10 compressor stage
11 Zuströmkanal  11 inflow channel
12 Dichtungsträger  12 seal carrier
13 Gehäuse  13 housing
14 Laufrad  14 impeller
15 Welle  15 wave
16 Nabe  16 hub
17 Deckscheibe  17 cover disk
18 Laufradschaufel  18 impeller blade
19 Strömungseintrittskante  19 flow inlet edge
20 Strömungsaustrittskante  20 flow outlet edge
21 Spalt  21 gap
22 Dichtung  22 seal
23 Dichtungsträger  23 seal carrier
24 Ringspalt  24 annular gap
25 Bohrung  25 hole
26 Dichtung  26 seal
27 Einlaufstern  27 inlet star
28 Kammer  28 chamber
29 Spalt  29 gap
30 Eintrittsleitschaufel  30 inlet guide vane

Claims

Ansprüche claims
1. Verdichterstufe, mit einem statorseitigen Ansaugstutzen, über welchen im Bereich der Verdichterstufe zu verdichtendes Medium in die Verdichterstufe einleitbar ist, mit einem statorseitigen Zuströmkanal (11), über welchen das zu verdichtende Medium ausgehend vom Ansaugstutzen in Richtung auf ein ro- torseitiges Laufrad (1 ) förderbar ist, wobei das Laufrad (14) eine radial innere Nabe (16), ein radial äußere Deckscheibe (17) und sich zwischen der Nabe1. Compressor stage, with a stator-side intake, via which in the compressor stage to be compressed medium in the compressor stage can be introduced, with a stator-side inflow channel (11), via which the medium to be compressed, starting from the intake manifold in the direction of a ro- torseitiges impeller ( 1) is conveyable, wherein the impeller (14) has a radially inner hub (16), a radially outer cover plate (17) and between the hub
(16) und der Deckscheibe (17) erstreckende Laufradschaufeln (18) aufweist, wobei zur Wirkdruckmessung an der Verdichterstufe an derselben eine Plus- Messstelle und eine Minus-Messstelle vorgesehen ist, dadurch gekennzeichnet, dass die Minus-Messstelle stromaufwärts des Laufrads (14) außerhalb des statorseitigen Zuströmkanals (11) in einem vom Zuströmkanal (11) abzweigenden Ringspalt (24) positioniert ist. (16) and the cover disc (17) extending impeller blades (18), wherein for the differential pressure measurement at the compressor stage on the same a plus measuring point and a minus measuring point is provided, characterized in that the minus measuring point upstream of the impeller (14) is positioned outside of the stator-side inflow channel (11) in an annular gap (24) branching off from the inflow channel (11).
2. Verdichterstufe nach Anspruch 1 , dadurch gekennzeichnet, dass der Ringspalt (24) unmittelbar stromaufwärts des Laufrads (14) vom statorseitigen Zuströmkanals (11) nach radial außen abzweigt. Second compressor stage according to claim 1, characterized in that the annular gap (24) immediately upstream of the impeller (14) from the stator-side inflow channel (11) branches off radially outward.
3. Verdichterstufe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Ringspalt (24) benachbart zum Laufrad (14) von einem statorseitigen Dichtungsträger (23), der eine mit der Deckscheibe ( 7) des rotorseitigen Laufrads3. compressor stage according to claim 1 or 2, characterized in that the annular gap (24) adjacent to the impeller (14) by a stator-side seal carrier (23), one with the cover plate (7) of the rotor-side impeller
(17) zusammenwirkende Dichtung (22) trägt, begrenzt ist. (17) carries co-operating seal (22) is limited.
4. Verdichterstufe nach Anspruch 3, dadurch gekennzeichnet, dass der Ringspalt (24) gegenüberliegend zum Laufrad (14) von einem statorseitigen Gehäuse (13) begrenzt ist. 4. compressor stage according to claim 3, characterized in that the annular gap (24) opposite to the impeller (14) by a stator-side housing (13) is limited.
5. Verdichterstufe nach Anspruch 3, dadurch gekennzeichnet, dass der Ringspalt (24) gegenüberliegend zum Laufrad (14) von einem statorseitigen Einlaufstern (27), der an einem statorseitigen Gehäuse (13) befestigt ist, begrenzt ist. 5. compressor stage according to claim 3, characterized in that the annular gap (24) opposite to the impeller (14) by a stator-side inlet star (27) which is fixed to a stator-side housing (13) is limited.
6. Verdichterstufe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der Ringspalt (24) kammerartig ausgebildet ist, wobei die Minus- Messstelle in einem kammerartigen Abschnitt (28) des Ringspalts (24) positioniert ist. 6. compressor stage according to one of claims 1 to 5, characterized in that the annular gap (24) is formed like a chamber, wherein the minus measuring point in a chamber-like portion (28) of the annular gap (24) is positioned.
7. Verdichterstufe nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass zu der Minus-Messstelle von radial außen eine Bohrung (25) führt, über die das an der Minus-Messstelle herrschende Druckniveau abgreifbar ist. 7. compressor stage according to one of claims 1 to 6, characterized in that to the minus measuring point from radially outside a bore (25) leads, via which the prevailing at the minus measuring point pressure level can be tapped.
8. Verdichterstufe nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die Plus-Messstelle im Bereich des Ansaugstutzens positioniert ist. 8. compressor stage according to one of claims 1 to 7, characterized in that the plus measuring point is positioned in the region of the intake.
9. Verdichterstufe nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass dieselbe eine Radialverdichterstufe ist. 9. compressor stage according to one of claims 1 to 8, characterized in that it 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 true EP3084227A1 (en) 2016-10-26
EP3084227B1 EP3084227B1 (en) 2018-10-31

Family

ID=53192507

Family Applications (1)

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

Country Status (6)

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

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Family Cites Families (11)

* Cited by examiner, † Cited by third party
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

Also Published As

Publication number Publication date
US10519975B2 (en) 2019-12-31
US20160319838A1 (en) 2016-11-03
CN105814317B (en) 2018-10-12
DE102014001998A1 (en) 2015-06-18
RU2634648C1 (en) 2017-11-02
EP3084227B1 (en) 2018-10-31
CN105814317A (en) 2016-07-27
WO2015090566A1 (en) 2015-06-25

Similar Documents

Publication Publication Date Title
EP3091179B1 (en) Rotor assembly for a fluid flow engine and compressor
EP3408503B1 (en) Turbomachinery with bladed diffuser
EP3056813A1 (en) Seal of an edge gap between effusion shingle of a gas turbine combustor
EP3184754B1 (en) Sensor assembly and measuring method for a turboengine
DE102013011350A1 (en) Gas turbine with high pressure turbine cooling system
DE10318852A1 (en) Main gas duct inner seal of a high pressure turbine
EP3091178A1 (en) Rotor drum for a fluid flow engine and compressor
DE102014012764A1 (en) Radial compressor stage
DE102007050916A1 (en) Stator arrangement for compressor of fluid conveying arrangement in gas turbine engine, has radial passage conduit formed in part of stator ring segment, where radial passage conduit is arranged adjacent to stator blade passage conduit
EP1706645B1 (en) Multi-stage friction vacuum pump
CH714432B1 (en) centrifugal compressor.
DE3031553A1 (en) GAS TURBINE WHEEL.
EP3084227B1 (en) Compressor stage
DE102016225018A1 (en) Centrifugal pump with radial impeller
DE4125763C2 (en)
WO2011036206A1 (en) Radial compressor diffuser
CH713634A2 (en) Compressor for a turbocharger.
CH714389B1 (en) centrifugal compressor.
DE102013005431B4 (en) axial flow machine
DE1525907A1 (en) Sealing construction for elements mounted rotatably relative to one another
EP3098452B1 (en) Turbo engine
EP2787180A1 (en) Guide blade assembly for a turbo engine
DE102016110269A1 (en) Axial turbine of a turbocharger and turbocharger
DE102020103022B4 (en) pump assembly
CH713304B1 (en) Centrifugal compressor and turbocharger.

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20160713

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIC1 Information provided on ipc code assigned before grant

Ipc: F04D 17/10 20060101ALI20180523BHEP

Ipc: F04D 29/16 20060101ALI20180523BHEP

Ipc: F04D 27/00 20060101AFI20180523BHEP

Ipc: F04D 29/42 20060101ALI20180523BHEP

INTG Intention to grant announced

Effective date: 20180619

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1059749

Country of ref document: AT

Kind code of ref document: T

Effective date: 20181115

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502014009957

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: MAN ENERGY SOLUTIONS SE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20181031

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190228

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190131

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190131

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190201

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190301

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502014009957

Country of ref document: DE

Owner name: MAN ENERGY SOLUTIONS SE, DE

Free format text: FORMER OWNER: MAN DIESEL & TURBO SE, 86153 AUGSBURG, DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502014009957

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181216

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20190131

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20181231

26N No opposition filed

Effective date: 20190801

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181216

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181231

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190131

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181031

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20141216

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181031

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20201211

Year of fee payment: 7

Ref country code: FR

Payment date: 20201223

Year of fee payment: 7

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1059749

Country of ref document: AT

Kind code of ref document: T

Effective date: 20191216

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20201224

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191216

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502014009957

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220701

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20211231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20211216