EP0439757B1 - Axialdrallregler für grossvolumige Radialverdichter - Google Patents

Axialdrallregler für grossvolumige Radialverdichter Download PDF

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Publication number
EP0439757B1
EP0439757B1 EP90124150A EP90124150A EP0439757B1 EP 0439757 B1 EP0439757 B1 EP 0439757B1 EP 90124150 A EP90124150 A EP 90124150A EP 90124150 A EP90124150 A EP 90124150A EP 0439757 B1 EP0439757 B1 EP 0439757B1
Authority
EP
European Patent Office
Prior art keywords
section
vanes
axial swirl
regulator according
axial
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.)
Revoked
Application number
EP90124150A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0439757A1 (de
Inventor
Reinhold Dr.-Ing. Herbst
Hans-Joachim Dipl.-Ing. Conrad
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.)
Howden Turbo GmbH
Original Assignee
Siemens Turbomachinery Equipment GmbH
Kuehnle Kopp and Kausch AG
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6398987&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0439757(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Siemens Turbomachinery Equipment GmbH, Kuehnle Kopp and Kausch AG filed Critical Siemens Turbomachinery Equipment GmbH
Publication of EP0439757A1 publication Critical patent/EP0439757A1/de
Application granted granted Critical
Publication of EP0439757B1 publication Critical patent/EP0439757B1/de
Anticipated expiration legal-status Critical
Revoked legal-status Critical Current

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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
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/56—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/563—Fluid-guiding means, e.g. diffusers adjustable specially adapted for elastic fluid pumps
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet

Definitions

  • the invention relates to an axial swirl controller for large-volume radial compressors, consisting of an axial diffuser with a ring extending axially to the loader axis, pivotable about radially oriented axes of rotation, which are essentially circular sections of such shape and division that they have the cross-section when the nozzle is completely closed almost completely cover a flow channel, which is arranged in a housing, the inner wall of which, viewed in the direction of flow, comprises a first jacket of a first cylinder section and a jacket of a spherical section, the spherical radius of the spherical section being equal to the radius of the first cylindrical section and the spherical section being nozzle-shaped into one passes over the second cylinder section, and with adjusting levers arranged on the shafts of the guide vanes projecting outward along the axes of rotation, which adjusting levers with an adjusting ring concentrically surrounding the housing via a coupling link ed are connected.
  • Such an axial swirl controller is known from DE-AS 1 628 232 for compressors with larger dimensions and is used for shifting the characteristic curve.
  • the flow channel in which the guide vanes of the axial guide apparatus are arranged, consists of two jacket sections with only a slightly different diameter and a spherical section lying between them. The diameter of this spherical section is larger than the radius of the larger cylindrical jacket section, ie the inlet-side flow channel is enlarged in the area of the guide vanes. This increase in diameter in the flow channel leads to turbulence and flow separation as well as to an increase in the vortex wake triggered by a speed jump on the guide vanes.
  • the second casing section adjoining the spherical section on the compressor side has an only insignificantly smaller diameter than the first cylindrical casing section, rapid suppression of the disturbance of the flow before entering the compressor is not possible, in particular since the compressor is arranged very close to the axial swirl regulator .
  • An axial swirl regulator is known from US Pat. No. 1 978 128, in which the guide vanes of the axial guide apparatus are arranged in a housing which transitions from a larger diameter to a smaller diameter in the manner of a polygon.
  • the axes of rotation of the guide vanes are inclined at an angle to the longitudinal axis of the flow channel and are guided in the center of the flow channel in a gear mechanism which causes a considerable disturbance of the flow.
  • the coupling of the individual guide vanes takes place via this gear to ensure synchronism.
  • the end of the axes of rotation of the individual guide vanes opposite the transmission is mounted approximately in the central section of the polygon housing, so that the front edge of the guide vanes runs approximately perpendicular to the central axis in the fully open state.
  • the polygonal shape of the housing wall means that the gap between the guide vanes and the lateral surface can be kept relatively small when the guide vanes are completely open, but because of the polygonal shape, the vanes, which are usually adjusted slightly towards the closed position, occur both at the front edge and at the operating position also relatively large gaps at the rear edge, which entail turbulence in the flow and cause a wake that is no longer eliminated into the subsequent compressor.
  • an axial swirl regulator for an exhaust gas turbocharger in which a spherical section adjoins the first cylinder section of the flow channel and merges into a second cylinder section, which is also the intake port of the exhaust gas turbocharger.
  • the nozzle-shaped spherical section results in a calming of the flow after the axial diffuser, in particular because of the relatively large diameter ratio of the inlet-side to the outlet-side cylinder section.
  • the axis of rotation of the respective guide blades is arranged in the blade leading edge. This one-sided mounting of the guide vanes leads to the occurrence of relatively large flow forces which not only make undesired but also very expensive structural measures necessary for axial-volume swirl regulators for large-volume compressors.
  • the invention is therefore based on the object of providing an axial swirl controller for large-volume radial compressors in which the flow experiences as little interference as possible from the guide apparatus and which is caused by the inevitable turbulence resulting vortex drag can be suppressed before reaching the compressor, so that a uniform flow across the entire cross section of the impeller is ensured.
  • the measures of the invention advantageously achieve that, with the lowest possible adjustment forces on the guide vanes, vortices and wake dents can be suppressed on the one hand by the acceleration of the flow in the region of the spherical section and on the other hand by the post-acceleration in the second cylinder section.
  • the restoring forces can be considerably reduced by creating a compensating surface, without having to accept the disadvantages of the prior art, which are necessary for a central arrangement of the Axis of rotation are inevitable.
  • a ratio of the diameters from the first cylinder section to the second cylinder section between 1.22 and 1.39 proves to be particularly expedient, the diameter of the second cylinder section being measured at the end of the section on the input side.
  • its lateral surface has an inclination with respect to an axially parallel lateral surface which extends between slightly greater than 0 ° to a maximum of 10 °.
  • An inclination of the lateral surface up to a maximum of 7 ° has proven to be particularly advantageous.
  • the guide vane adjustment which is carried out from an adjusting ring, uses an adjusting lever and a coupling member, the adjusting lever located on the axis of rotation of the guide vane running with its longitudinal axis in the direction of the longitudinal extension of the guide vane.
  • an actuating lever and a coupling element By using an actuating lever and a coupling element, it is possible to ensure, by suitable angular assignment of the actuating lever to the coupling element, that the most suitable torque can be worked in the adjustment range of the guide vanes that is normally assigned, i.e. the lowest adjustment forces are required in this adjustment range.
  • the adjustment ring is fixed by stops in such a way that an adjustment range of the guide vanes between 15 ° and -90 ° is possible, the guide device being completely closed at a position of -90 °.
  • a pointer is also assigned to the adjusting lever, with which the position of the guide vane can be read on a scale.
  • Fig. 1 the housing 10 of an axial swirl controller is shown schematically, which is flanged in the plane II-II to the housing of a radial compressor with an impeller 12.
  • a compressor housing is shown above the center line, which differs from the illustration below the center line. The difference results from different impeller sizes and the design of the section of the housing shown between level II-II and level A-A, which is different with respect to the slope of the inner casing. Accordingly, the associated impeller is dimensioned differently.
  • the housing 10 of the axial compressor consists of a first cylinder section 15 between the entry plane E and the plane K-K and a spherical section 16 between the plane K-K and the assembly plane II-II.
  • the second cylinder section 17 adjoins this assembly plane, which extends to the entry plane A-A of an impeller 12. This is followed by a section of the compressor housing 18 assigned to the impeller.
  • a guide device 20 is attached within the housing 10 of the axial swirl controller, which consists of a ring that extends radially to the compressor axis 21 and can be pivoted about radially oriented axes of rotation guide vanes 22.
  • the axes of rotation 23 of the guide vanes 22 lie in the plane K-K and run perpendicular to the compressor axis 21.
  • the spherical section 16 of the housing 10 has a spherical radius which is equal to the radius of the first cylinder section 15, so that there is a nozzle-like reducing cross section for the spherical section which, in the assembly plane II-II, merges with a continuously decreasing diameter deviating from the spherical radius.
  • the second cylinder section 17 connects, the associated lateral surface of which has an inclination between slightly greater than 0 ° to 10 ° in relation to an axially parallel lateral surface.
  • the guide vanes 22, which are rotatably mounted in the plane KK, are supported on one side in such a way that the guide vane area is divided by the axis of rotation 23 in a ratio of 1/3: 2/3, the axes of rotation being arranged in the diameter plane in the transition region from the first cylinder section 15 to the ball section 16 . Because of this structure, only the wider blade half engages in the spherical section 16 in the fully open state, the end edge running along a circular line being flush with a small gap along the lateral surface of the spherical section 16. This practically prevents the formation of vortices or wake dents on the compressor side of the guide vanes.
  • the one-sided mounting of the guide vanes after the first third of the guide vane surface results in a particularly favorable compromise with regard to the force acting on the guide vanes due to the flow and the development of turbulence within the flow, since this is inevitably between the axis of rotation and the front end point of the circular end edge gap forming in the area of the first cylinder section 15 acts as a disturbance of the flow and triggers turbulence.
  • the small swirls in the flow which have an effect in this gap region are suppressed in the region of the axial swirl regulator by the nozzle-shaped reduction in the cross section in the spherical section 16, so that there is an essentially uninterrupted flow when exiting the diffuser.
  • FIG. 2 shows details of the adjusting device for the guide apparatus.
  • an adjusting ring 31 is guided with the aid of rolling elements 32.
  • An adjusting arm 33 is connected to the adjusting ring 31, on which an adjusting motor (not shown) acts, which displaces the adjusting ring in the circumferential direction.
  • Stops 34 are attached to the housing 10, which ensure that the adjusting ring can only be rotated within a range which permits a guide vane rotation between 15 ° to -90 °, the guide apparatus being completely closed at a position of -90 °. This corresponds to the representation according to FIG. 2.
  • an adjusting lever 25 is fastened on the axis of rotation 23 of the guide vanes and is connected to the adjusting ring 31 via a coupling member 26.
  • the coupling member 26 is spatially rotatably connected to the adjusting ring 31 on the one hand and to the adjusting lever 25 on the other hand, the geometry of the arrangement of the levers relative to one another being such that when the guide vanes are in the middle position in the usual range of rotation, the coupling member forms an angle of approximately 90 ° with the adjusting lever has, so that the force in the coupling member is minimal and a particularly balanced control game is possible in this area.
  • This central position of the control range is roughly assigned to an angular position of the guide vanes from 0 ° to 30 °.
  • FIG. 5 shows the position of the actuating lever and of the coupling element relative to one another for the closed state of the guide apparatus in the extended position and for the completely open state of the guide apparatus in a dash-dotted line.
  • this illustration shows a scale 36, which is fastened to the housing 10 and, via an adjusting lever 25 provided with a pointer 37, displays the angular position of the individual guide vanes in the guide apparatus.
  • an adjusting lever 25 is provided with the pointer 37 extending in the longitudinal direction.
  • the articulated connection between the coupling member and the adjusting ring 31 on the one hand and the adjusting lever 25 on the other hand is designed in a conventional manner.
  • the adjusting lever 25 is braced on the axis of rotation 23 in a conventional manner.
  • the explained guide apparatus can be used with the same adjusting elements for a left-handed as well as a right-handed compressor. To adapt to an opposite direction of rotation, only a mirror-image assembly is necessary.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP90124150A 1990-01-29 1990-12-13 Axialdrallregler für grossvolumige Radialverdichter Revoked EP0439757B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4002548 1990-01-29
DE4002548A DE4002548C3 (de) 1990-01-29 1990-01-29 Axialdrallregler für großvolumige Radialverdichter

Publications (2)

Publication Number Publication Date
EP0439757A1 EP0439757A1 (de) 1991-08-07
EP0439757B1 true EP0439757B1 (de) 1993-09-01

Family

ID=6398987

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90124150A Revoked EP0439757B1 (de) 1990-01-29 1990-12-13 Axialdrallregler für grossvolumige Radialverdichter

Country Status (6)

Country Link
US (1) US5108256A (fi)
EP (1) EP0439757B1 (fi)
DE (2) DE4002548C3 (fi)
DK (1) DK0439757T3 (fi)
ES (1) ES2045736T3 (fi)
FI (1) FI910003A (fi)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4117025A1 (de) * 1991-05-24 1992-11-26 Halberg Maschbau Gmbh & Co Drallregler fuer kreiselpumpen
EP1719887A1 (de) * 2005-05-04 2006-11-08 ABB Turbo Systems AG Auflade-Regelung für Verbrennungsmotor
GB0821089D0 (en) * 2008-11-19 2008-12-24 Ford Global Tech Llc A method for improving the performance of a radial compressor
US9435220B2 (en) * 2010-01-16 2016-09-06 Borgwarner Inc. Turbocharger control linkage with reduced heat flow
EP2971596B1 (en) * 2013-03-10 2020-07-15 Rolls-Royce Corporation Gas turbine engine and corresponding method
DE102014212606B4 (de) * 2014-06-30 2020-12-17 Ford Global Technologies, Llc Kraftfahrzeug und Luftfilterbox
CN110631944B (zh) * 2019-09-27 2022-08-05 国家电网有限公司 一种水下材料冲刷立体效果实验装置及方法
US11885351B2 (en) 2019-10-31 2024-01-30 Daikin Industries, Ltd. Inlet guide vane actuator assembly

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1978128A (en) * 1932-03-14 1934-10-23 Clarage Fan Company Vortex control
US2606713A (en) * 1948-04-26 1952-08-12 Snecma Adjustable inlet device for compressors
US3362625A (en) * 1966-09-06 1968-01-09 Carrier Corp Centrifugal gas compressor
US4022540A (en) * 1975-10-02 1977-05-10 General Electric Company Frangible airfoil structure
US4013377A (en) * 1975-10-08 1977-03-22 Westinghouse Electric Corporation Intermediate transition annulus for a two shaft gas turbine engine
US3973869A (en) * 1975-10-28 1976-08-10 Allis-Chalmers Corporation Turbine in-take baffles
US4428714A (en) * 1981-08-18 1984-01-31 A/S Kongsberg Vapenfabrikk Pre-swirl inlet guide vanes for compressor
US4681509A (en) * 1984-07-23 1987-07-21 American Davidson, Inc. Variable inlet fan assembly
DE3613857A1 (de) * 1986-04-24 1987-10-29 Kuehnle Kopp Kausch Ag Axialdrallregler fuer einen abgasturbolader fuer verbrennungsmotoren

Also Published As

Publication number Publication date
DE4002548C3 (de) 1995-01-26
DK0439757T3 (da) 1994-02-21
FI910003A0 (fi) 1991-01-02
DE59002565D1 (de) 1993-10-07
US5108256A (en) 1992-04-28
ES2045736T3 (es) 1994-01-16
EP0439757A1 (de) 1991-08-07
DE4002548C2 (fi) 1991-11-28
FI910003A (fi) 1991-07-30
DE4002548A1 (de) 1991-08-08

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