CN101761512B - Asymmetric self-circulation processing machine box of centrifugal compressor with arc-shaped grooving positions - Google Patents

Asymmetric self-circulation processing machine box of centrifugal compressor with arc-shaped grooving positions Download PDF

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CN101761512B
CN101761512B CN 201010110230 CN201010110230A CN101761512B CN 101761512 B CN101761512 B CN 101761512B CN 201010110230 CN201010110230 CN 201010110230 CN 201010110230 A CN201010110230 A CN 201010110230A CN 101761512 B CN101761512 B CN 101761512B
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annular groove
centrifugal compressor
self
compressor
processing machine
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CN101761512A (en
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郑新前
林韵
张扬军
马场隆弘
玉木秀明
杨名洋
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Tsinghua University
IHI Corp
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IHI Corp
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Priority to JP2011553812A priority patent/JP5430683B2/en
Priority to PCT/JP2011/052269 priority patent/WO2011099416A1/en
Priority to US13/578,101 priority patent/US9151297B2/en
Priority to EP11742160.2A priority patent/EP2535595B1/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

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

Abstract

An asymmetric self-circulation processing machine box of a centrifugal compressor with arc-shaped grooving positions 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 distances Sr between a front end surface of the pumping ring groove and a front edge of a main flow blade are distributed in an arc 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 arc-shaped grooving positions, compared with an axisymmetric self-circulation processing machine box with coincident grooving positions in the circumference direction, the stable working range of the centrifugal compressor can be greatly increased, and the efficiency remains almost unchanged.

Description

Slotting position is the asymmetric self-loopa processor box of centrifugal compressor that circular arc distributes
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, the 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 it is the effective ways that improve the gas compressor stable operation range that casing is handled.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 casing processing structure generally is made up of suction annular groove 1, water conservancy diversion annular groove 2 and backflow annular groove 3, and its main structure parameters has: suction annular groove front-end face is with respect to the position S of main flow blade inlet edge 4 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 front-end face is with respect to the position S of main flow blade 4 leading edges rBackflow pressure reduction and return flow have directly been determined, to expanding having the greatest impact of steady effect.Therefore design suitable suction annular groove position S rValue is that non-axisymmetric self-loopa processor casing structure is realized the optimum key that expands steady effect in the distribution that makes progress in week.
Summary of the invention
The object of the invention is, by designing a kind of suction annular groove position distribution of asymmetric self-loopa processor casing structure, promptly aspirate the annular groove front-end face apart from the leading edge of compressor impeller main flow blade apart from S rDistribution 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:
Slotting position is the asymmetric self-loopa processor box of centrifugal compressor that circular arc distributes, contain the gas compressor volute, on described 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 front-end face of described suction annular groove apart from the leading edge of compressor impeller main flow blade apart from S rUpwards be the circular arc distribution in week, the central angle of arc section is α, and its span is: 0＜α≤30 °; The radius of arc section is R, determines that according to the impeller diameter D of centrifugal compressor the span of R is:
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 2 and backflow annular groove.
The present invention compared with prior art, have the following advantages and the high-lighting effect: adopting slotting position proposed by the invention is the asymmetric self-loopa processor box of centrifugal compressor that circular arc distributes, can improve the stable operation range of centrifugal-flow compressor significantly than the consistent in a circumferential direction axisymmetric self-loopa processor box of slotting position, 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 volute schematic representation.
Fig. 5 is the corresponding different initial angle θ of designed suction annular groove form 0S rBe worth distribution schematic diagram in a circumferential direction.
Fig. 6 is nested with suction annular groove schematic representation.
Fig. 7 is S in the example rValue distribution schematic diagram in a circumferential direction.
Fig. 8 is initial angle θ in the example 0Position view.
The gas compressor performance comparison figure that Fig. 9 a and Fig. 9 b are that to adopt slotting position be the asymmetric self-loopa processor box that distributes of circular arc when adopting axisymmetric self-loopa processor box with no casing processing.
Embodiment
Below in conjunction with accompanying drawing principle of the present invention, structure and working procedure are further described.
Slotting position is the asymmetric self-loopa processor box of centrifugal compressor that circular arc distributes, contain the gas compressor volute, on described 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 front-end face of described suction annular groove apart from the leading edge of compressor impeller main flow blade 4 apart from S rUpwards be the circular arc distribution in week, the central angle of arc section is α, and its span is: 0＜α≤30 °; The radius of arc section is R, determines that according to the impeller diameter D of centrifugal compressor the span of R is:
Figure GSA00000030689300022
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 0Suction annular groove position S rValue circular arc in a circumferential direction distributes.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 the individual different initial angle θ corresponding to n 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 position S rValue circular arc in a circumferential direction distributes, as shown in Figure 5.
Fig. 6 is the schematic representation that is nested with suction annular groove 1 on 6.The designed upper and lower edge of suction annular groove that distributes by circular arc in a circumferential direction is curved surface, indicates as dotted line among Fig. 6.
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 slotting position that circular arc distributes 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 size, adopting slotting position is the example of the asymmetric self-loopa processor box of centrifugal compressor of circular arc distribution with the raising stable operation range.
Processor box S is handled in the asymmetric self-loopa of this gas compressor rValue being distributed as shown in Figure 7 in a circumferential direction.Initial angle point θ 0=90 °, its position as shown in Figure 8.
Fig. 9 a is the asymmetric self-loopa processor box and the consistent in a circumferential direction axisymmetric self-loopa processor box of employing slotting position that circular arc distributes with Fig. 9 b for this centrifugal compressor adopts slotting position of the present invention, and does not have the gas compressor performance comparison figure that casing is handled.
Pass through performance comparison, adopting slotting position of the present invention as can be known is that the asymmetric self-loopa processor box of centrifugal compressor that circular arc distributes is handled with respect to no casing, and adopt the consistent in a circumferential direction centrifugal compressor axisymmetric self-loopa processor box of slotting position can improve the stable operation range of gas compressor significantly, it is constant substantially to keep efficient simultaneously.

Claims (2)

1. the asymmetric self-loopa processor box of centrifugal compressor, contain the gas compressor volute, on described 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 front-end face of described suction annular groove upwards distributes for circular arc in week apart from the distance of the leading edge of compressor impeller main flow blade (4), the central angle of circular arc is α, and its span is: 0＜α≤30 °; The radius of circular arc is R, determines that according to the impeller diameter D of centrifugal compressor the span of R is:
Figure FDA0000048199580000011
2. according to the asymmetric self-loopa processor box of the described centrifugal compressor 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), forms described water conservancy diversion annular groove (2) and backflow annular groove (3) between the internal face of described shell and the outer wall that is nested with.
CN 201010110230 2010-02-09 2010-02-09 Asymmetric self-circulation processing machine box of centrifugal compressor with arc-shaped grooving positions Active CN101761512B (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN 201010110230 CN101761512B (en) 2010-02-09 2010-02-09 Asymmetric self-circulation processing machine box of centrifugal compressor with arc-shaped grooving positions
JP2011553812A JP5430683B2 (en) 2010-02-09 2011-02-03 Centrifugal compressor with non-axisymmetric self-circulating casing treatment
PCT/JP2011/052269 WO2011099416A1 (en) 2010-02-09 2011-02-03 Centrifugal compressor using an asymmetric self-recirculating casing treatment
US13/578,101 US9151297B2 (en) 2010-02-09 2011-02-03 Centrifugal compressor having an asymmetric self-recirculating casing treatment
EP11742160.2A EP2535595B1 (en) 2010-02-09 2011-02-03 Centrifugal compressor using an asymmetric self-recirculating casing treatment

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5466118A (en) * 1993-03-04 1995-11-14 Abb Management Ltd. Centrifugal compressor with a flow-stabilizing casing
CN101012838A (en) * 2007-02-02 2007-08-08 清华大学 Centrifugal compressor having vane jet orifice
CN101092976A (en) * 2007-07-30 2007-12-26 北京航空航天大学 Synergic action device of controlling flow of airbleed inside blades of diffuser in centrifugal compressor
EP1902953A1 (en) * 2006-09-20 2008-03-26 TURBOMECA, Société dite: Device for soundproofing a gas turbine helicopter engine and engine obtained using same

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5466118A (en) * 1993-03-04 1995-11-14 Abb Management Ltd. Centrifugal compressor with a flow-stabilizing casing
EP1902953A1 (en) * 2006-09-20 2008-03-26 TURBOMECA, Société dite: Device for soundproofing a gas turbine helicopter engine and engine obtained using same
CN101012838A (en) * 2007-02-02 2007-08-08 清华大学 Centrifugal compressor having vane jet orifice
CN101092976A (en) * 2007-07-30 2007-12-26 北京航空航天大学 Synergic action device of controlling flow of airbleed inside blades of diffuser in centrifugal compressor

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