EP0590254B1 - Verstellbarer Radialdiffusor - Google Patents

Verstellbarer Radialdiffusor Download PDF

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Publication number
EP0590254B1
EP0590254B1 EP93111495A EP93111495A EP0590254B1 EP 0590254 B1 EP0590254 B1 EP 0590254B1 EP 93111495 A EP93111495 A EP 93111495A EP 93111495 A EP93111495 A EP 93111495A EP 0590254 B1 EP0590254 B1 EP 0590254B1
Authority
EP
European Patent Office
Prior art keywords
diffuser
adjustment
radial
adjustment members
plates
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.)
Expired - Lifetime
Application number
EP93111495A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0590254A1 (de
Inventor
Albrecht Weigel
Uwe Schmidt-Eisenlohr
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.)
MTU Aero Engines GmbH
Original Assignee
MTU Motoren und Turbinen Union Muenchen GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by MTU Motoren und Turbinen Union Muenchen GmbH filed Critical MTU Motoren und Turbinen Union Muenchen GmbH
Publication of EP0590254A1 publication Critical patent/EP0590254A1/de
Application granted granted Critical
Publication of EP0590254B1 publication Critical patent/EP0590254B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F05D2250/52—Outlet

Definitions

  • the invention relates to an adjustable radial diffuser for a radial compressor, which has adjusting elements with blades arranged in a diffuser ring space and evenly distributed over the diffuser circumference with the pitch angle ⁇ , the adjusting elements for changing the narrow cross section Q between the blades each having an adjusting axis V parallel to the longitudinal axis L. are pivotable.
  • Such a radial diffuser has the task of reducing the flow velocity supplied to the gas flow through the compressor rotor and thereby converting its kinetic energy into static pressure. Since compressors have very different pressure designs at different speeds, the volume flow at the wheel outlet changes differently than at the wheel inlet. It is therefore necessary to adapt the diffusers to the different volume flows in order to achieve an optimal energy conversion efficiency under all operating conditions.
  • the pressure-throughput characteristic in a radial compressor depends on the adaptation of the diffuser capacity, which is determined by the diffuser narrow surface, to that of the rotor delivered volume flow. These narrow diffuser surfaces are defined as the smallest surface normal to the direction of flow between two adjacent diffuser blades.
  • the diffuser narrow surfaces should be as large as possible, and correspondingly smaller at the maximum pressure ratio.
  • the diffuser blades adjustable in different ways in order to be able to vary the said diffuser surfaces.
  • the object is achieved in that the adjusting elements have a U-shaped or H-shaped cross-section, circular-sector-shaped plates attached to the blade roots on both sides forming the legs and the diffuser blade forming the web.
  • the design according to the invention has the advantage of avoiding blade gaps between the blade pressure side and the blade suction side, where there is a high pressure difference. A harmful flow on the back of the plates is insignificant due to the small pressure difference in the circumferential direction. It has proven favorable for the efficiency that the blades can be pivoted as a whole, so that the area ratio and length / width ratio of the diffuser channels can be in the optimal range.
  • the radial diffuser in the inlet area is free of steps that are transverse to the main flow direction, which eliminates additional aerodynamic losses.
  • these can preferably be pivoted synchronously and in the same direction by means of an adjusting mechanism.
  • a simple mounting of the adjustment elements in the diffuser housing via bearing journals concentric to the adjustment axes ensures exact adjustability even under thermal stress.
  • the space between the plate sides of adjacent adjustment elements that opens or closes during the adjustment movement and extends in the main flow direction is optimized in terms of flow by the preferred embodiment of the invention.
  • the width of the free space always remains constant over the length of adjacent plate sides.
  • An aerodynamically unfavorable inclination of the free space in relation to the flow direction can hereby be avoided over the entire adjustment range.
  • a further, improved embodiment of the invention is given by the features of claims 8 and 9, whereby the diffuser channels of the throttled radial diffuser, i. H. remain in the position of the adjusting elements belonging to the smallest narrow cross section, without free spaces between the plates and without its influence on the flow. If the adjustment elements are not throttled, i.e. H. at the maximum size of the narrow cross section, the plate exit edges lie on a common circle, so that a stepless diffuser outlet is formed.
  • a radial compressor 1 which rotates about the longitudinal axis L of the compressor.
  • the delivered gas flow is conveyed into the area of the diffuser blades 4 of the radial diffuser 5 via the radial blades 3 distributed around the circumference of the radial compressor 1.
  • the air is then collected in the air collecting spiral 6 and fed to a further compressor or a combustion chamber connected downstream.
  • the radial compressor 1 drive energy supplied from the outside is thus converted into potential and kinetic energy of the flow medium.
  • the kinetic energy is then partially converted into potential energy in the form of pressure by deceleration.
  • the delay mentioned is determined by the contour of the diffuser blades 4.
  • the radial diffuser 5 consists of a plurality of adjustment elements 7 distributed uniformly on the circumference, each with a diffuser blade 4.
  • An adjusting element 7, as shown in FIGS. 3, 4 and 5, is formed from two circular sector-shaped plates 8 with the sector angle and a diffuser blade 4, the plates 8 of an adjusting element arranged parallel to each other having a diffuser blade 4 between their radial edge 9 enclose themselves and thus give the adjusting element 7 a U-shaped shape.
  • An alternative embodiment of an adjusting element 7 with an H-shaped configuration is shown in FIG. 6.
  • the diffuser blade 4 extends between the two radial edges 9a of the plates 8.
  • the placement of the diffuser blade 4 in the adjusting element 7 is selected such that the diffuser blade 4 extends over its blade depth along a radially extending edge 9a and the pressure side 10 of the diffuser blade 4 points into the interior of the U-shaped adjusting element .
  • the circular segment-shaped plates 8 have a round end 11 at their radially inner end, that is to say at their narrowest point, and in this respect deviate from an exact circular sector.
  • the diffuser blade 4 closes with its leading edge 12 in the transition region between the end 11 and the edge 9a.
  • the center of the round termination 11 lies on the adjustment axis V of the adjustment element 7.
  • the adjustment axis V is thus perpendicular to the plane of the plates 8 of an adjustment element.
  • the adjustment axis V is perpendicular to the bisector W of the plates 8 of each adjustment element 7, as shown in FIGS. 2 and 3.
  • the adjusting elements 7 are arranged obliquely in the diffuser ring space, the element angle ⁇ measured between the bisector W and a radial R which is perpendicular to the Compressor longitudinal axis L and the adjustment axis V is 90 ° - 180 °, but here is approximately 120 °.
  • the element angle ⁇ of each adjusting element 7 can be varied by the same amount.
  • the adjustment axis V of all adjustment elements 7 are arranged parallel and at the same radial distance a to the longitudinal axis L of the compressor, as can be seen in FIGS. 1 and 2.
  • the adjusting elements 7, which are evenly spaced apart from one another with the pitch angle ⁇ in the circumferential direction of the radial diffuser 5, can be seen in FIG. 2.
  • the diffuser channels 13 are limited on the one hand by the interior of the adjusting elements 7 and on the other hand by the suction side 14 of the diffuser blade 4 of the adjacent adjusting element 7.
  • the radial diffuser 5 can be throttled or unthrottled by pivoting movement S of the adjusting elements 7 in the same direction about its adjusting axis V. Throttling is achieved by pivoting the adjusting elements 7 toward the interior of the diffuser I and dethrottling is accordingly achieved by pivoting the exterior of the diffuser A. In the throttled state, this results in a minimum narrow cross-section Q min (see FIG.
  • the plates 8 of adjacent adjusting elements 7 lie tightly and continuously along their edges 9a.
  • the adjusting elements 7 are spaced apart from one another along adjacent plates 8, ie a gap 16 is formed over the edge length between the edges 9a of adjacent plates 8.
  • the arcuately shaped radially outer edges 9b of the plates 8 come to rest on a cylindrical surface Z which is concentric with the longitudinal axis L of the compressor, this cylindrical surface Z being part of the diffuser housing 16.
  • the arc radius of the outer edges 9b thus corresponds to that Radius of this cylinder surface Z.
  • the plate ends 17a and 8b show adjustment elements 7 in an overlapping interlocking arrangement, the free plate ends 17a opposite the diffuser blade 4 and the plate ends 17b of the adjacent adjustment element 7 provided with a diffuser blade 4 within their pivoting range of the adjustment elements 7 reach around.
  • the plate ends 17b each have a recess 18 extending into the plate plane, the depth t of which transversely to the plate plane corresponds to the plate thickness d of the adjacent plate 8 for receiving the plate 8 or its free plate end 17a, as shown in FIGS. 3 and 5 evident.
  • the width of the recess 18 thus corresponds to the maximum overlap width of the adjusting elements, as is the case when the adjusting elements 7 are in a throttled position (see FIG. 8a).
  • the recess 18 runs parallel to the edge 9a of the plate end 17a of the adjacent adjusting element 7.
  • the adjusting elements 7 are each provided with bevels 19 in the diffuser channels 13 between the diffuser blade 7 and the plates 8 to compensate for the recesses 18. The bevels 19 thus narrow the diffuser channel 13 towards the diffuser blade 4.
  • FIG. 9 shows the mounting of the adjusting elements 7 between two diffuser walls 20 of the diffuser housing 16 which are perpendicular to the longitudinal axis L of the compressor 8 are largely stepless to the nozzle walls 20. Between the nozzle walls 20 and the plates 8, a seal 21, which extends in the radial direction, is arranged to avoid cross-flows.
  • the plates 8 are outside the diffuser channel 13 with the adjusting axis V coaxial bearing pin 22 which are received in holes in the nozzle walls 20.
  • a plate 8 of an adjustment element has an adjustment pin 23, which is coupled to an adjustment device 24.
  • the nozzle walls 20 are connected to one another via webs 25.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP93111495A 1992-07-30 1993-07-17 Verstellbarer Radialdiffusor Expired - Lifetime EP0590254B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4225126A DE4225126C1 (ja) 1992-07-30 1992-07-30
DE4225126 1992-07-30

Publications (2)

Publication Number Publication Date
EP0590254A1 EP0590254A1 (de) 1994-04-06
EP0590254B1 true EP0590254B1 (de) 1996-01-24

Family

ID=6464416

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93111495A Expired - Lifetime EP0590254B1 (de) 1992-07-30 1993-07-17 Verstellbarer Radialdiffusor

Country Status (5)

Country Link
US (1) US5342168A (ja)
EP (1) EP0590254B1 (ja)
AT (1) ATE133473T1 (ja)
DE (1) DE4225126C1 (ja)
ES (1) ES2083229T3 (ja)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7147433B2 (en) * 2003-11-19 2006-12-12 Honeywell International, Inc. Profiled blades for turbocharger turbines, compressors, and the like
US20080286136A1 (en) * 2007-05-17 2008-11-20 Purvines Stephen H Fan housing
US8511981B2 (en) * 2010-07-19 2013-08-20 Cameron International Corporation Diffuser having detachable vanes with positive lock
US8683791B2 (en) 2010-08-20 2014-04-01 Toyota Motor Engineering & Manufacturing North America, Inc. Method and system for homogenizing exhaust from an engine

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2985427A (en) * 1955-11-25 1961-05-23 Gen Electric Adjustable blading for fluid flow machines
US2904307A (en) * 1956-10-01 1959-09-15 Crane Co Cooling turbine
US3069070A (en) * 1961-11-14 1962-12-18 Worthington Corp Diffuser vane system for turbomachinery
GB1036485A (en) * 1964-06-05 1966-07-20 Bristol Siddeley Engines Ltd Improvements in or relating to a reversible, inward flow, independent power turbine
CH492130A (de) * 1968-08-20 1970-06-15 Escher Wyss Ag Das Laufrad eines Zentrifugalverdichters koaxial umschliessender, für die Anströmung mit Überschallgeschwindigkeit bestimmter Leitapparat
DE1952423A1 (de) * 1969-10-17 1971-05-27 Garrett Corp Schaufeldichtung
SE382342B (sv) * 1973-06-18 1976-01-26 United Turbine Ab & Co Avloppsdiffusor for centrifugalkompressor
DE2433726A1 (de) * 1974-07-13 1976-01-29 Motoren Turbinen Union Turboverdichter-austrittsleitvorrichtung
GB1510629A (en) * 1974-08-08 1978-05-10 Penny Turbines Ltd N Centrifugal compressor or centripetal turbine
US3963369A (en) * 1974-12-16 1976-06-15 Avco Corporation Diffuser including movable vanes
JPS5677598A (en) * 1979-11-30 1981-06-25 Nissan Motor Co Ltd Variable-position diffuser for centrifugal compressor
US4325673A (en) * 1980-03-10 1982-04-20 General Motors Corporation Variable vane seal
US4770605A (en) * 1981-02-16 1988-09-13 Mitsubishi Jukogyo Kabushiki Kaisha Diffuser device in a centrifugal compressor and method for manufacturing the same
JPS5815797A (ja) * 1981-07-22 1983-01-29 Nissan Motor Co Ltd 可変デイフユ−ザ
US4642026A (en) * 1983-07-26 1987-02-10 Ruff John D Centrifugal compressor with adjustable diffuser
US4527949A (en) * 1983-09-12 1985-07-09 Carrier Corporation Variable width diffuser

Also Published As

Publication number Publication date
DE4225126C1 (ja) 1993-04-01
EP0590254A1 (de) 1994-04-06
ES2083229T3 (es) 1996-04-01
ATE133473T1 (de) 1996-02-15
US5342168A (en) 1994-08-30

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