CN101761511B - Asymmetric self-circulation processing machine box of centrifugal compressor with parabolic grooving widths - Google Patents

Asymmetric self-circulation processing machine box of centrifugal compressor with parabolic grooving widths Download PDF

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CN101761511B
CN101761511B CN 201010110225 CN201010110225A CN101761511B CN 101761511 B CN101761511 B CN 101761511B CN 201010110225 CN201010110225 CN 201010110225 CN 201010110225 A CN201010110225 A CN 201010110225A CN 101761511 B CN101761511 B CN 101761511B
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annular groove
centrifugal compressor
self
processing machine
machine box
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CN101761511A (en
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郑新前
杨名洋
张扬军
马场隆弘
玉木秀明
林韵
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Tsinghua University
IHI Corp
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Tsinghua University
IHI Corp
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Priority to CN 201010110225 priority Critical patent/CN101761511B/en
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Priority to US13/578,137 priority patent/US9234526B2/en
Priority to JP2011553813A priority patent/JP5430684B2/en
Priority to EP11742161.0A priority patent/EP2535596B1/en
Priority to PCT/JP2011/052272 priority patent/WO2011099417A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F04D29/685—Inducing localised fluid recirculation in the stator-rotor interface

Abstract

An asymmetric self-circulation processing machine box of a centrifugal compressor with parabolic grooving widths relates to a processing machine box of the centrifugal compressor and belongs to the technical field of impeller machineries. A self-circulation channel is formed by installing a pumping ring groove, a reflux ring groove and a flow guiding ring groove on the wall surface of a turbine shell of the compressor, the widths br values of the pumping ring groove are distributed in a parabola shape in the circumference direction to optimize the expanding stability effect of the asymmetric self-circulation processing machine box on the centrifugal compressor. By adopting the asymmetric self-circulation processing machine box of the centrifugal compressor with the parabolic grooving widths, compared with an axisymmetric self-circulation processing machine box with coincident grooving widths in the circumference direction, the stable working range of the centrifugal compressor can be greatly increased, and the efficiency remains almost unchanged.

Description

Groove width is the asymmetric self-loopa processor box of parabolical centrifugal compressor
Technical field
The present invention relates to a kind of centrifugal-flow compressor processor box, belong to impeller machinery technical field.Can be used for turbomachines such as the pressurized machine centrifugal compressor of various uses, industrial centrifugal compressor and aviation centrifugal compressor.
Background technique
Impeller type gas compressors such as centrifugal-flow compressor have advantages such as efficient height, volume weight is light, running is steady, but its operating mode are limited in scope with respect to reciprocating compressor.Phenomenons such as large scale flow separation appear in interior flow field under the centrifugal-flow compressor low discharge operating mode, the unstable operation phenomenon occurs, cause stall even surge, directly cause compressor efficiency and pressure ratio sharply to descend, life-span seriously shortens, even directly damages in the short time.Therefore people have taked a lot of methods to postpone the generation of wild effects such as compressor stall, to enlarge its stable operation range.
Generally believe that at present processor box is the effective ways that improve the gas compressor stable operation range.But traditional processor casing structure is generally axially symmetric structure.And when gas compressor is in off-design behaviour, because the circumferential distortion that the axial asymmetry of centrifugal compressor volute has caused impeller outlet to flow, thereby influence the flow parameter of upstream, cause the circumferential flow parameter of compressor impeller and vaneless diffuser inside to present nonaxisymmetry.Traditional axisymmetric processor casing structure can't be considered the nonaxisymmetrical characteristics of gas compressor interior flow field, therefore can't make processor box realize that the optimum that makes progress in full week expands steady effect.Therefore need to adopt nonaxisymmetrical self-loopa processor box, expand steady effect to be implemented in the optimum that makes progress in full week.
As shown in Figure 1, nonaxisymmetrical self-loopa processor box generally comprises suction annular groove 1, water conservancy diversion annular groove 2 and backflow annular groove 3, and its main structure parameters has: suction annular groove 1 is with respect to main flow blade inlet edge 4 position S r, suction annular groove width b r, position S is introduced in gas backstreaming f, width b is introduced in gas backstreaming f, bypass height h b, bypass width b bDeng.Studies show that suction annular groove width b rTo expanding steady effect bigger influence is arranged.Therefore design the suction annular groove width b on the suitable circumferencial direction rValue distributes, and is that non-axisymmetric self-loopa processor box is realized the optimum key that expands steady effect.
Summary of the invention
The object of the invention is, by designing a kind of suction annular groove width b of asymmetric self-loopa processor casing structure rValue distribution in a circumferential direction is to optimize asymmetric self-loopa processor box to the steady effect of the expansion of centrifugal compressor.
Technological scheme of the present invention is as follows:
Groove width is the asymmetric self-loopa processor box of parabolical centrifugal compressor, contain the gas compressor volute, on gas compressor volute wall, be provided with suction annular groove, water conservancy diversion annular groove and backflow annular groove, described suction annular groove, water conservancy diversion annular groove and backflow annular groove form self-circulation channel, it is characterized in that: the width b of described suction annular groove rBe parabolic distribution, i.e. b in a circumferential direction r=A (α D-β D) 2+ A 0,
Wherein A is this parabolical characteristic parameter, determines that according to the impeller diameter D of centrifugal compressor the span of A is
Figure GSB00000407827400021
α represents to aspirate the circumference angle of annular groove, is the independent variable of formula, and the definitional domain of α is: θ 0≤ α≤θ 0+ 360 °, θ 0Be circumferential initial angle, span is 0 °≤θ 0≤ 360 °; β is the circumference angle of this parabolic distribution in extreme point place correspondence, promptly when α=β, and b rExtreme value A is arranged 0, A 0Span is:
Figure GSB00000407827400022
In the technique scheme, described gas compressor volute is made up of with being nested with shell, and described suction annular groove 1 is arranged on the wall that is nested with, and the internal face of described shell and the outer wall that is nested with form described water conservancy diversion annular groove and backflow annular groove.
The present invention compared with prior art, have the following advantages and the high-lighting effect: adopting groove width proposed by the invention is the asymmetric self-loopa processor box of parabolical centrifugal compressor, can improve the stable operation range of centrifugal compressor significantly than the consistent in a circumferential direction axisymmetric self-loopa processor box of groove width, it is constant substantially to keep efficient simultaneously.
Description of drawings
Fig. 1 is the self-circulation channel schematic representation.
Fig. 2 is the shell mechanism schematic representation.
Fig. 3 is nested with structural representation.
Fig. 4 is a gas compressor turbocharger housing structure schematic representation.
Fig. 5 is the corresponding different initial angle θ of designed suction annular groove form 0B rBe worth distribution schematic diagram in a circumferential direction.
Fig. 6 is nested with suction annular groove schematic representation.
Fig. 7 is initial angle θ in the example 0Position view.
Fig. 8 a and Fig. 8 b are the gas compressor performance comparison figure when adopting groove width to be parabolical asymmetric self-loopa processor box and employing axisymmetric self-loopa processor box and the processing of no casing.
Embodiment
Below in conjunction with accompanying drawing principle of the present invention, structure and working procedure are further described.
Groove width is the asymmetric self-loopa processor box of parabolical centrifugal compressor, contain the gas compressor volute, on gas compressor volute wall, be provided with suction annular groove 1, water conservancy diversion annular groove 2 and backflow annular groove 3, described suction annular groove, water conservancy diversion annular groove and backflow annular groove form self-circulation channel, the width b of described suction annular groove rBe parabolic distribution, i.e. b in a circumferential direction r=A (α D-β D) 2+ A 0,
Wherein A is this parabolical characteristic parameter, determines that according to the impeller diameter D of centrifugal compressor the span of A is
Figure GSB00000407827400023
α represents to aspirate the circumference angle of annular groove, is the independent variable of formula, and the definitional domain of α is: θ 0≤ α≤θ 0+ 360 °, θ 0Be circumferential initial angle, span is 0 °≤θ 0≤ 360 °; β is the circumference angle of this parabolic distribution in extreme point place correspondence,, promptly when α=β, b rExtreme value A is arranged 0, A 0Span is:
Figure GSB00000407827400024
Described gas compressor volute is by shell 5 and be nested with 6 and form, and described suction annular groove 1 is arranged on and is nested with on 6 the wall, and the internal face of described shell forms described water conservancy diversion annular groove 2 and backflow annular groove 3 with the outer wall that is nested with.
Fig. 2 is the structural representation of shell 5.Fig. 3 is nested with 6 structural representation.Shell is combined into the gas compressor volute with being nested with, as shown in Figure 4.
Set casing 5, and the rotation be nested with 6, the relative position of the two assembling is changed, can obtain different initial angle θ 0The width b of suction annular groove 2 rValue parabolic distribution in a circumferential direction.Described shell and being nested with by screw 7 connects to form, and at the shell uniform n screw hole that made progress last week, can obtain corresponding to n initial angle θ 0Distribution curve, determine optimum initial angle θ by the gas compressor performance test 0For example, have 4 screw holes among Fig. 2 on the shell 5 altogether, therefore can obtain four kinds of different suction annular groove width b rValue parabolic distribution in a circumferential direction, as shown in Figure 5.
Fig. 6 is the schematic representation that is nested with suction annular groove 1 on 6.The lower limb of the designed suction annular groove that distributes parabolically in a circumferential direction is a curved surface.
In the centrifugal compressor working procedure, during low flow rate condition, air is flowed out through water conservancy diversion annular groove 2 and backflow annular groove 3 by suction annular groove 1 in the self-circulation channel.Concrete working procedure and principle are: the gas in self-loopa processor box suction annular groove 1 suction blade tip zone, slotting position place, through water conservancy diversion annular groove 2, penetrated by backflow annular groove 3.The pumping action of blade tip zone, suction annular groove 1 cross-notching position gas causes the tip clearance leakage vortex to be sucked annular groove 1 and draws, and the passage of leakage flow is blocked; The gas compressor inlet is injected in backflow, because communicating of flowing in the annular groove realized the flow uniformity of gas compressor inlet, eliminates the passage shock wave; Backflow has increased inlet flow rate, and the blade inlet positive incidence is reduced, and the pumping action of aspirating annular groove 1 has simultaneously weakened the back pressure of gas compressor aditus laryngis, and adverse pressure gradient reduces, and has effectively suppressed the separation of blade surface boundary layer.Use the suction annular groove groove width of parabolic distribution on the circumferencial direction, feasible corresponding in a circumferential direction fluting place backflow better effects if, thus more effectively utilize the effect that refluxes, make the stable operation range of gas compressor enlarge.
In the nearly operating mode of stopping up, air penetrates from suction annular groove 1 through backflow annular groove 3, water conservancy diversion annular groove 2 in the self-circulation channel.Backflow annular groove 3 makes inlet circumferentially go up flow communication, thereby gas compressor inlet flow uniformity is increased, and has weakened the inlet shock wave; The jet of suction annular groove 1 strengthens negotiability, thereby has expanded the obstruction border.But, because nearly obstruction operating mode suction power deficiency, so this processor box is unobvious to the expansion on stall border to the expansion of stopping up the border.
Below be the centrifugal compressor at a certain concrete size, adopting groove width is the example of the asymmetric self-loopa processor box of centrifugal compressor of parabolic distribution with the raising stable operation range.
The asymmetric self-loopa processor box of this gas compressor b rValue is distributed as: b r=-0.00008 (α-182 °) 2+ 6.8, initial phase site θ 0=90 °, its position as shown in Figure 7.
Fig. 8 a is the parabolical asymmetric self-loopa processor box axisymmetric self-loopa processor box consistent in a circumferential direction with adopting groove width with Fig. 8 b for employing groove width of the present invention and does not have the gas compressor performance comparison figure that casing is handled.
Pass through performance comparison, adopting groove width of the present invention as can be known is that the asymmetric self-loopa processor box of parabolical centrifugal compressor is handled with respect to no casing, and adopt the consistent in a circumferential direction centrifugal compressor axisymmetric self-loopa processor box of groove width can improve the stable operation range of gas compressor significantly, it is constant substantially to keep efficient simultaneously.

Claims (2)

1. groove width is the asymmetric self-loopa processor box of parabolical centrifugal compressor, contain the gas compressor volute, on gas compressor volute wall, be provided with suction annular groove (1), water conservancy diversion annular groove (2) and backflow annular groove (3), described suction annular groove, water conservancy diversion annular groove and backflow annular groove form self-circulation channel, it is characterized in that: the width b of described suction annular groove rBe parabolic distribution, i.e. b in a circumferential direction r=A (α D-β D) 2+ A 0,
Wherein A is this parabolical characteristic parameter, determines that according to the impeller diameter D of centrifugal compressor the span of A is
Figure FSB00000407827300011
α represents to aspirate the circumference angle of annular groove, is the independent variable of formula, and the definitional domain of α is:
θ 0≤ α≤θ 0+ 360 °, θ 0Be circumferential initial angle, span is 0 °≤θ 0≤ 360 °; β is the circumference angle of this parabolic distribution in extreme point place correspondence, promptly when α=β, and b rExtreme value A is arranged 0, A 0Span is:
Figure FSB00000407827300012
2. be the asymmetric self-loopa processor box of parabolical centrifugal compressor according to the described groove width of claim 1, it is characterized in that: described gas compressor volute is by shell (5) and be nested with (6) and form, described suction annular groove (1) is arranged on the wall that is nested with (6), and the internal face of described shell and the outer wall that is nested with form described water conservancy diversion annular groove (2) and backflow annular groove (3).
CN 201010110225 2010-02-09 2010-02-09 Asymmetric self-circulation processing machine box of centrifugal compressor with parabolic grooving widths Active CN101761511B (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN 201010110225 CN101761511B (en) 2010-02-09 2010-02-09 Asymmetric self-circulation processing machine box of centrifugal compressor with parabolic grooving widths
US13/578,137 US9234526B2 (en) 2010-02-09 2011-02-03 Centrifugal compressor having an asymmetric self-recirculating casing treatment
JP2011553813A JP5430684B2 (en) 2010-02-09 2011-02-03 Centrifugal compressor with non-axisymmetric self-circulating casing treatment
EP11742161.0A EP2535596B1 (en) 2010-02-09 2011-02-03 Centrifugal compressor using an asymmetric self-recirculating casing treatment
PCT/JP2011/052272 WO2011099417A1 (en) 2010-02-09 2011-02-03 Centrifugal compressor using an asymmetric self-recirculating casing treatment

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CN102606529B (en) * 2012-03-28 2014-04-30 杭州诺沃能源科技有限公司 Processing case structure for gas compressor of aircraft engine
CN103967812B (en) * 2014-04-29 2016-04-20 西北工业大学 A kind of return flow type is to turning adsorption pressure mechanism of qi
CN105065328B (en) * 2015-08-06 2017-11-14 中国北方发动机研究所(天津) A kind of double flute for centrifugal compressor automatically adjusts casing processing unit

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0614014A1 (en) * 1993-03-04 1994-09-07 ABB Management AG Radial compressor with a flow stabilising casing
CN101092977A (en) * 2007-07-23 2007-12-26 北京航空航天大学 Method for designing box of processor
CN201176968Y (en) * 2007-11-30 2009-01-07 中国航空工业第一集团公司沈阳发动机设计研究所 Halting cell type casing treatment and compressor
CN101451544A (en) * 2007-11-30 2009-06-10 中国航空工业第一集团公司沈阳发动机设计研究所 Processing casing and air compressor
CN101566171A (en) * 2009-05-21 2009-10-28 北京航空航天大学 Axial inclined slot and reverse vortex shallow slot circumferential non-axisymmetrical combination type processor box
CN101614222A (en) * 2009-07-23 2009-12-30 上海交通大学 Centrifugal compressor case

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0614014A1 (en) * 1993-03-04 1994-09-07 ABB Management AG Radial compressor with a flow stabilising casing
CN101092977A (en) * 2007-07-23 2007-12-26 北京航空航天大学 Method for designing box of processor
CN201176968Y (en) * 2007-11-30 2009-01-07 中国航空工业第一集团公司沈阳发动机设计研究所 Halting cell type casing treatment and compressor
CN101451544A (en) * 2007-11-30 2009-06-10 中国航空工业第一集团公司沈阳发动机设计研究所 Processing casing and air compressor
CN101566171A (en) * 2009-05-21 2009-10-28 北京航空航天大学 Axial inclined slot and reverse vortex shallow slot circumferential non-axisymmetrical combination type processor box
CN101614222A (en) * 2009-07-23 2009-12-30 上海交通大学 Centrifugal compressor case

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