CN101737359A - Asymmetric self-circulation processing case with slotting position of sine distribution for centrifugal compressor - Google Patents
Asymmetric self-circulation processing case with slotting position of sine distribution for centrifugal compressor Download PDFInfo
- Publication number
- CN101737359A CN101737359A CN 201010110250 CN201010110250A CN101737359A CN 101737359 A CN101737359 A CN 101737359A CN 201010110250 CN201010110250 CN 201010110250 CN 201010110250 A CN201010110250 A CN 201010110250A CN 101737359 A CN101737359 A CN 101737359A
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- China
- Prior art keywords
- annular groove
- centrifugal compressor
- self
- processing case
- compressor
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Classifications
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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
The invention discloses an asymmetric self-circulation processing case with slotting position of sine distribution for a centrifugal compressor, relating to a processing case of a centrifugal compressor, and belonging to the technical field of impeller machineries. A self-circulation channel is formed by arranging a pumping and sucking ring slot, a reflow ring slot and a guide ring slot on the wall surface of a compressor volute casing, and the distance Sr from the front end face of the pumping and sucking ring slot to the front edge of a main stream blade is in parabola distribution on the circumference direction to optimize the stability enhancing effect of the asymmetric self-circulation processing case on the centrifugal compressor. By adopting the asymmetric self-circulation processing case with slotting position of parabola distribution for a centrifugal compressor, compared with the shaft symmetric self-circulation processing case with consistent slotting width on the circumference direction, the stable working range of the centrifugal compressor can be greatly improved while the efficiency is maintained unchangeable. In addition, the asymmetric self-circulation processing case has an easy processed structure.
Description
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 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: the suction annular groove is with respect to the position S of main flow blade 4 leading edges
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
bWith bypass width b
bStudies show that the suction annular groove 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 distribution in a circumferential direction is that non-axisymmetric self-loopa processor casing structure 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 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 the centrifugal compressor of sinusoidal distribution, 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 front-end face of described suction annular groove apart from the leading edge of main flow blade 4 apart from S
rBe sinusoidal distribution, i.e. S in a circumferential direction
r=Asin (α+θ
0)+A
0,
A wherein
0Be the mean value of suction annular groove position, determine A according to the impeller diameter D of centrifugal compressor
0Span be 0.05≤| A
0/ D|＜0.2; The amplitude of A for distributing, 0.1＜| A/A
0|＜0.35; θ
0Be initial angle, span is 0 °≤θ
0≤ 360 °; α is the circumferential angle of casing, is the independent variable of formula, and definitional domain is: θ
0≤ α≤θ
0+ 360 °.
In the technique scheme, 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.
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 of sinusoidal distribution, 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 initial angle θ in the example
0Position view.
Fig. 8 is that the employing slotting position is the asymmetric self-loopa processor box of sinusoidal distribution and the gas compressor performance comparison figure of no casing processing.
Fig. 9 is that to adopt slotting position be the gas compressor performance comparison figure of the consistent in a circumferential direction axisymmetric self-loopa processor box of asymmetric self-loopa processor box and the employing slotting position of sinusoidal distribution.
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 the centrifugal compressor of sinusoidal distribution, 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 front-end face of described suction annular groove apart from the leading edge of main flow blade 4 apart from S
rBe sinusoidal distribution, i.e. S in a circumferential direction
r=Asin (α+θ
0)+A
0,
A wherein
0Be the mean value of suction annular groove position, determine A according to the impeller diameter D of centrifugal compressor
0Span be 0.05≤| A
0/ D|＜0.2; The amplitude of A for distributing, 0.1＜| A/A
0|＜0.35; θ
0Be initial angle, span is 0 °≤θ
0≤ 360 °; α is the circumferential angle of casing, is the independent variable of formula, and definitional domain is: θ
0≤ α≤θ
0+ 360 °.
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, make the two the assembling relative position change, can obtain different initial angle θ
0The sinusoidal distribution of suction annular groove position.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 the sinusoidal distribution of four kinds of different suction annular groove positions, as shown in Figure 5.
Fig. 6 is the schematic representation that is nested with suction annular groove 1 on 6.According to geometric proof as can be known, designed be the plane by the upper and lower edge of suction annular groove of sinusoidal distribution in a circumferential direction, indicate as dotted line among Fig. 6.This characteristic makes designed suction annular groove process easily and adjust: change when changing the inclination of this straight line around the axle center and put S
rThe amplitude A that distributes; When this straight line of upper and lower translation, promptly corresponding different suction annular groove position S
rThe suction annular groove mean place A that distributes
0
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 of sinusoidal 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, the self-loopa machine is handled the interior air of casket passage through backflow annular groove 3, water conservancy diversion annular groove 2, penetrates from suction annular groove 1.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 slotting position is the example of the asymmetric self-loopa processor box of centrifugal compressor of sinusoidal distribution with the raising stable operation range.
The asymmetric self-loopa processor box of this gas compressor S
rValue being distributed as in a circumferential direction: S
r=sin (α+180 °)+4, initial angle θ
0=180 °, its position as shown in Figure 7.
Fig. 8 is the asymmetric self-loopa processor box of centrifugal compressor and no casing handling property comparison diagram of sinusoidal distribution for this centrifugal compressor adopts slotting position of the present invention." G " sign adopts centrifugal compressor performance MAP figure of the present invention among the figure; The centrifugal compressor MAP figure that the no casing of " No CT " sign is handled.
Fig. 9 for this centrifugal compressor adopt slotting position be sinusoidal distribution asymmetric self-loopa processor box with adopt slotting position at the gas compressor performance comparison figure of consistent axisymmetric self-loopa processor box that makes progress in week." G " sign adopts centrifugal compressor performance MAP figure of the present invention among the figure; The centrifugal compressor MAP figure that " C " sign adopts the consistent in a circumferential direction axisymmetric self-loopa casing of slotting position to handle.
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 of sinusoidal distribution is handled than 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. slotting position is the asymmetric self-loopa processor box of centrifugal compressor of sinusoidal distribution, 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 front-end face of described suction annular groove apart from the leading edge of main flow blade (4) apart from S
rBe sinusoidal distribution, i.e. S in a circumferential direction
r=Asin (α+θ
0)+A
0,
A wherein
0Be the mean value of suction annular groove position, determine A according to the impeller diameter D of centrifugal compressor
0Span be 0.05≤| A
0/ D|＜0.2; The amplitude of A for distributing, 0.1＜| A/A
0|＜0.35; θ
0Be initial angle, span is 0 °≤θ
0≤ 360 °; α is the circumferential angle of casing, is the independent variable of formula, and definitional domain is: θ
0≤ α≤θ
0+ 360 °.
2. according to the described slotting position of claim 1 the asymmetric self-loopa processor box of centrifugal compressor of sinusoidal distribution, 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).
Priority Applications (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010110250 CN101737359B (en) | 2010-02-09 | 2010-02-09 | Asymmetric self-circulation processing case with slotting position of sine distribution for centrifugal compressor |
| EP11742162.8A EP2535597B1 (en) | 2010-02-09 | 2011-02-03 | Centrifugal compressor using an asymmetric self-recirculating casing treatment |
| US13/578,163 US10273973B2 (en) | 2010-02-09 | 2011-02-03 | Centrifugal compressor having an asymmetric self-recirculating casing treatment |
| PCT/JP2011/052273 WO2011099418A1 (en) | 2010-02-09 | 2011-02-03 | Centrifugal compressor using an asymmetric self-recirculating casing treatment |
| JP2011553814A JP5430685B2 (en) | 2010-02-09 | 2011-02-03 | Centrifugal compressor with non-axisymmetric self-circulating casing treatment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010110250 CN101737359B (en) | 2010-02-09 | 2010-02-09 | Asymmetric self-circulation processing case with slotting position of sine distribution for centrifugal compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101737359A true CN101737359A (en) | 2010-06-16 |
| CN101737359B CN101737359B (en) | 2011-06-15 |
Family
ID=42461262
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201010110250 Active CN101737359B (en) | 2010-02-09 | 2010-02-09 | Asymmetric self-circulation processing case with slotting position of sine distribution for centrifugal compressor |
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| CN (1) | CN101737359B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104053911A (en) * | 2012-01-23 | 2014-09-17 | 株式会社Ihi | Centrifugal compressor |
| CN107614886A (en) * | 2015-10-29 | 2018-01-19 | 三菱重工业株式会社 | Volute and centrifugal compressor |
| CN109109103A (en) * | 2018-09-22 | 2019-01-01 | 连云港军振木业有限公司 | The wood processing equipment of environmental protection |
| CN109667794A (en) * | 2017-10-17 | 2019-04-23 | 博格华纳公司 | Multi-piece type compressor housing for turbocharger |
-
2010
- 2010-02-09 CN CN 201010110250 patent/CN101737359B/en active Active
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104053911A (en) * | 2012-01-23 | 2014-09-17 | 株式会社Ihi | Centrifugal compressor |
| CN104053911B (en) * | 2012-01-23 | 2016-06-22 | 株式会社Ihi | Centrifugal compressor |
| US9816524B2 (en) | 2012-01-23 | 2017-11-14 | Ihi Corporation | Centrifugal compressor |
| CN107614886A (en) * | 2015-10-29 | 2018-01-19 | 三菱重工业株式会社 | Volute and centrifugal compressor |
| US11078922B2 (en) | 2015-10-29 | 2021-08-03 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Scroll casing and centrifugal compressor |
| CN109667794A (en) * | 2017-10-17 | 2019-04-23 | 博格华纳公司 | Multi-piece type compressor housing for turbocharger |
| EP3473862A1 (en) * | 2017-10-17 | 2019-04-24 | Borgwarner Inc. | Multi-piece compressor housing for a turbocharger |
| US10519974B2 (en) | 2017-10-17 | 2019-12-31 | Borgwarner Inc. | Multi-piece compressor housing for a turbocharger |
| CN109109103A (en) * | 2018-09-22 | 2019-01-01 | 连云港军振木业有限公司 | The wood processing equipment of environmental protection |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101737359B (en) | 2011-06-15 |
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