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CN109812453A - Centrifugal compressor - Google Patents

Centrifugal compressor Download PDF

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Publication number
CN109812453A
CN109812453A CN201811391436.2A CN201811391436A CN109812453A CN 109812453 A CN109812453 A CN 109812453A CN 201811391436 A CN201811391436 A CN 201811391436A CN 109812453 A CN109812453 A CN 109812453A
Authority
CN
China
Prior art keywords
secondary flow
impeller
centrifugal compressor
flow channel
seen
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.)
Pending
Application number
CN201811391436.2A
Other languages
Chinese (zh)
Inventor
H.贝内奇克
C.海因茨
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.)
Everllence SE
Original Assignee
MAN Energy Solutions SE
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 MAN Energy Solutions SE filed Critical MAN Energy Solutions SE
Publication of CN109812453A publication Critical patent/CN109812453A/en
Pending 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
    • F04D29/441—Fluid-guiding means, e.g. diffusers 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • 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
    • 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)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)

Abstract

A kind of centrifugal compressor (10), the especially centrifugal compressor of exhaust-driven turbo-charger exhaust-gas turbo charger: it has impeller (11)；With fixed shell (13)；With the primary flow channel (14) limited by shell (13), for supplying medium to be compressed towards the direction of impeller (11)；And with the secondary flow chamber (15) for being arranged in primary flow channel (14) radial outside, the secondary flow chamber (15) is defined by contoured wall (16) and the boundary of primary flow channel (14), and the secondary flow chamber (15) is connected to primary flow channel (14) via secondary flow opening (18) in the region of impeller (11).As seen in the meridional section, secondary flow chamber (15) is connected to secondary flow opening (18) of primary flow channel (14) relative to radial direction by oblique or obliquely set via it in the region of impeller (11).

Description

Centrifugal compressor
Technical field
The present invention relates to a kind of centrifugal compressors of preamble according to claim 1.
Background technique
From the exhaust-driven turbo-charger exhaust-gas turbo charger of preamble according to claim 1 a kind of known to 2 194 277 A1 of EP from Core type compressor.Therefore, 2 194 272 A1 of EP shows the centrifugal compressor with rotary blade and fixed shell.Shell Body limits primary flow channel, so that the side in impeller boots up the medium of compression.On the outside of primary flow channel, it is disposed with by taking turns Wide wall defines the secondary flow chamber with the boundary of primary flow channel.According to 2 194 277 A1 of EP, secondary flow chamber is from main flow The suction areas in channel starts the secondary flow extended up in the region of impeller opening.In the region of impeller, secondary flow chamber Room is connected to primary flow channel via secondary flow opening.The pillar of connection contoured wall extends in secondary flow chamber, the contoured wall Define the boundary of primary flow channel Yu secondary flow chamber.According to 2 194 272 A1 of EP, secondary flow chamber is in the region of impeller It is connected to primary flow channel via secondary flow opening, is prolonged in radial directions as seen in the meridional section, secondary flow is open It stretches.
Via such secondary flow chamber for being connected to primary flow channel, centrifugal compressor can be improved in certain degree The characteristic pattern stability of machine and thus operation behavior.
By the throttling of the enhancing of centrifugal compressor, even if working media to be compressed entering in impeller within the compressor Also be subjected in the domain of mouth region it is enough pressure accumulated so that working media is via secondary flow chamber and flow direction on the contrary in mainstream It is recycled in dynamic channel, wherein in this way, under recirculation mode, be able to achieve the reduced conveying speed with compressor The aerodynamic stability of rate.
If there is the major demands of the throughput to centrifugal compressor, then pressure is generated in the entrance area of impeller Drop, as a result, via secondary flow on the direction that working media substitutes its own on the flow direction by primary flow channel Chamber, so that in whether flowing through secondary flow chamber under recirculation mode but under bypass mode.Then can as a result, Realize the high delivery rate of centrifugal compressor.
In the presence of the demand of the further characteristic pattern stability for improving centrifugal compressor.In particular, exist along further drop The direction of low delivery rate increases stable operation range and increases the demand of the air inlet capacity of centrifugal compressor.
Summary of the invention
Based on this, the purpose of the present invention is create a kind of novel centrifugal compressor.The purpose according to right by wanting 1 centrifugal compressor is asked to solve.According to the present invention, seen in the meridional section, secondary flow chamber is via it in the area of impeller The secondary flow opening that primary flow channel is connected in domain obliquely or is obliquely set relative to radial direction.It is arranged by these It applies, can further improve the stability of the working range of centrifugal compressor.It in particular, can be about the conveying speed further decreased Rate and about air inlet capacity increase working range.
According to advantageous another improvement, seen in meridional section, secondary flow chamber is in the region of impeller via its company The secondary flow opening for being connected to primary flow channel includes and angle of the radial direction between 10 ° and 80 °, preferably in 10 ° and 70 ° Between angle, particularly preferably the angle between 20 ° and 70 °, the most preferably angle between 20 ° and 60 °.In meridian It seen in section, is open these angular ranges relative to inclined using secondary flow, especially for providing into one It walks reduced delivery rate and in order to extend air inlet capacity, can particularly preferably extend the steady operation model of centrifugal compressor It encloses.
Detailed description of the invention
Other advantageous embodiment of the invention is obtained from dependent claims and the following description.Example of the invention is implemented Example is described in more detail by attached drawing, but not limited to this.
It shows that
Fig. 1 is the schematic meridional section by centrifugal compressor according to the present invention.
Specific embodiment
Fig. 1 show taken by the section of the exemplary preferred embodiment of centrifugal compressor 10 according to the present invention it is transversal Face.
Centrifugal compressor 10 includes the rotary blade 11 with multiple moving blades 12.In addition, centrifugal compressor 10 Including fixed shell 13.The shell 13 of centrifugal compressor 10 limits the primary flow channel 14 for being used for medium to be compressed, so as to Medium to be compressed is guided via primary flow channel 14 on the direction of impeller 11.In 14 outside of primary flow channel, shell 13 is limited Determine secondary flow chamber 15.The contoured wall 16 for having been described as annular web defines the side of primary flow channel 14 Yu secondary flow chamber 15 Boundary.
Secondary flow chamber 15 extends up to the region into impeller 11 from the section in 11 upstream of impeller.Therefore, Fig. 1 shows Out, it is formed with the first secondary flow opening 17 in 11 upstream of impeller, via first secondary flow opening 17, in medium to be compressed Flow direction on the secondary flow chamber 15 seen be connected to primary flow channel 14 in 11 upstream of impeller.In the region of impeller 11 It is formed with the dynamic opening 18 of second subsidiary stream, via the dynamic opening 18 of the second subsidiary stream, secondary flow chamber 15 is in the region of impeller 11 It is connected to primary flow channel 14.
Pillar 19 extends in secondary flow chamber 15.Via pillar 19, contoured wall 16 is connected to shell 13.
Secondary flow chamber 15 is open 18 in the region of impeller 11 via its secondary flow for being connected to primary flow channel 14 It is obliquely set as seen in meridional section relative to radial direction R according to the present invention.
As seen in the meridional section, secondary flow chamber 15 is connected to primary flow channel via it in the region of impeller 11 14 secondary flow opening 18 includes the angle [alpha] with radial direction R.The angle [alpha] is between 10 ° and 80 °, preferably in 10 ° and 70 ° Between, particularly preferably between 20 ° and 70 °, and most preferably between 20 ° and 60 °.
In especially preferred embodiment of the invention, angle [alpha] reaches 25 ° ± 15 °, preferentially 25 ° ± 10 °, and excellent First 25 ° ± 5 °.
By according to an embodiment of the invention, secondary flow chamber 15 to be connected to main flow via it in the region of impeller logical The secondary flow opening 18 in road 14 is able to achieve following advantages.
When close to the surge limit of centrifugal compressor, in the region of secondary flow chamber 15 in centrifugal compressor The recycling of medium to be compressed is advantageous.In Fig. 1, arrow I makes recycling of the working media by secondary flow chamber 15 17 side as it can be seen that the secondary flow opening 18 i.e. since in the region of impeller 11 starts to be open towards the secondary flow in 11 upstream of impeller To the direction is opposite with by the flow direction of the visible main flow of arrow III in Fig. 1.
When close to the capacity limitation or choking limit of centrifugal compressor, the bypass flow by secondary flow chamber 15 is It is advantageous, wherein such bypass flow is visible by the arrow II in Fig. 1.The bypass flow II be used in choking limit or High delivery rate is provided in the region of capacity limitation, and since the secondary flow of 11 upstream of impeller opening 17 towards in leaf The direction of secondary flow opening 18 in the region of wheel 11 is guided.The bypass flow II can be almost without restriction effect the case where Under be supplied to main flow.Therefore, surge limit can not only be extended and capacity limitation or choking limit can also be extended.
The working range of centrifugal compressor can finally be extended significantly as a result,.It is according to the present invention centrifugal utilizing In the turbocharger of compressor, it can improve efficiency.In addition, faster respondent behavior during being able to achieve load switching.
Secondary flow opening 18 in the region of impeller 11 can lead to shell 13 and to the transition profile of contoured wall 16 It crosses sharp edge or rounded corner is carried out.
Secondary flow opening 18 is preferentially implemented as the aperture recycled in circumferential direction.
Reference signs list:
10 centrifugal compressors
11 impellers
12 moving blades
13 shells
14 primary flow channels
15 secondary flow chambers
16 contoured walls
17 secondary flows opening
18 secondary flows opening
19 pillars

Claims (6)

1.一种离心式压缩机(10)，特别是废气涡轮增压器的离心式压缩机，1. a centrifugal compressor (10), particularly the centrifugal compressor of an exhaust gas turbocharger, 带有旋转叶轮(11)，with rotating impeller (11), 带有固定壳体(13)，with fixed housing (13), 带有由所述壳体(13)限定的主流动通道(14)，用于在所述叶轮(11)的方向上供给待压缩的介质，with a main flow channel (14) defined by the housing (13) for supplying the medium to be compressed in the direction of the impeller (11), 带有布置在所述主流动通道(14)径向外侧的副流动腔室(15)，所述副流动腔室(15)由轮廓壁(16)界定与所述主流动通道(14)的边界，并且所述副流动腔室(15)在所述叶轮(11)的区域中经由副流动开口(18)连接至所述主流动通道(14)，with a secondary flow chamber (15) arranged radially outside said primary flow channel (14), said secondary flow chamber (15) being delimited by a contoured wall (16) from said primary flow channel (14) boundary, and the secondary flow chamber (15) is connected to the primary flow channel (14) via secondary flow openings (18) in the region of the impeller (11), 其特征在于，It is characterized in that, 在子午截面中所见，所述副流动腔室(15)在所述叶轮(11)的区域中经由其连接至所述主流动通道(14)的所述副流动开口(18)相对于径向方向被斜向或倾斜地设定。The secondary flow chamber ( 15 ) is in the region of the impeller ( 11 ) via which the secondary flow opening ( 18 ) is connected to the primary flow channel ( 14 ) relative to the diameter, seen in a meridian section The direction is set obliquely or obliquely. 2.根据权利要求1所述的离心式压缩机，其特征在于，在子午截面中所见，所述副流动腔室(15)在所述叶轮(11)的区域中经由其连接至所述主流动通道(14)的所述副流动开口(18)包括与所述径向方向在10°与80°之间的角度。2. Centrifugal compressor according to claim 1, characterized in that the secondary flow chamber (15) is connected via it to the said impeller (11), seen in a meridional section Said secondary flow opening (18) of the main flow channel (14) comprises an angle with said radial direction of between 10° and 80°. 3.根据权利要求2所述的离心式压缩机，其特征在于，在子午截面中所见，所述副流动开口(18)包括与所述径向方向在10°与70°之间的角度。3. A centrifugal compressor according to claim 2, characterised in that the secondary flow opening (18) comprises an angle with the radial direction between 10° and 70°, seen in a meridional section . 4.根据权利要求3所述的离心式压缩机，其特征在于，在子午截面中所见，所述副流动开口(18)包括与所述径向方向在20°与70°之间的角度。4. A centrifugal compressor according to claim 3, characterized in that the secondary flow opening (18) comprises an angle with the radial direction between 20° and 70°, seen in a meridional section . 5.根据权利要求4所述的离心式压缩机，其特征在于，在子午截面中所见，所述副流动开口(18)包括与所述径向方向在20°与60°之间的角度。5. A centrifugal compressor according to claim 4, characterized in that the secondary flow opening (18) comprises an angle with the radial direction between 20° and 60°, seen in a meridional section . 6.根据权利要求1至5中的任一项所述的离心式压缩机，其特征在于，在待压缩的介质的流动方向上所见的，所述副流动腔室(15)经由另一副流动开口(17)在所述叶轮(11)上游连接至所述主流动通道(14)。6. The centrifugal compressor according to any one of claims 1 to 5, characterized in that, as seen in the flow direction of the medium to be compressed, the secondary flow chamber (15) passes through another A secondary flow opening (17) is connected to the main flow channel (14) upstream of the impeller (11).
CN201811391436.2A 2017-11-21 2018-11-21 Centrifugal compressor Pending CN109812453A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017127421.9 2017-11-21
DE102017127421.9A DE102017127421A1 (en) 2017-11-21 2017-11-21 centrifugal compressors

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US (1) US20190154041A1 (en)
JP (1) JP2019094897A (en)
KR (1) KR20190058324A (en)
CN (1) CN109812453A (en)
CH (1) CH714389B1 (en)
DE (1) DE102017127421A1 (en)

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JP7220097B2 (en) 2019-02-27 2023-02-09 三菱重工業株式会社 Centrifugal compressor and turbocharger

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US20150198163A1 (en) * 2014-01-15 2015-07-16 Honeywell International Inc. Turbocharger With Twin Parallel Compressor Impellers And Having Center Housing Features For Conditioning Flow In The Rear Impeller
US20160160756A1 (en) * 2013-07-24 2016-06-09 Borgwarner Inc. Turbocharger combining axial flow turbine with a compressor stage utilizing active casing treatment

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Publication number Priority date Publication date Assignee Title
US20030138317A1 (en) * 1998-12-10 2003-07-24 Mark Barnett Casing treatment for a fluid compressor
CN101749283A (en) * 2008-12-05 2010-06-23 Abb涡轮系统有限公司 Compressor stabilizer
CN103703219A (en) * 2011-07-20 2014-04-02 Ihi供应系统国际有限责任公司 Turbine for an exhaust-gas turbocharger
US20160160756A1 (en) * 2013-07-24 2016-06-09 Borgwarner Inc. Turbocharger combining axial flow turbine with a compressor stage utilizing active casing treatment
US20150198163A1 (en) * 2014-01-15 2015-07-16 Honeywell International Inc. Turbocharger With Twin Parallel Compressor Impellers And Having Center Housing Features For Conditioning Flow In The Rear Impeller

Also Published As

Publication number Publication date
US20190154041A1 (en) 2019-05-23
CH714389A2 (en) 2019-05-31
KR20190058324A (en) 2019-05-29
CH714389B1 (en) 2021-12-15
JP2019094897A (en) 2019-06-20
DE102017127421A1 (en) 2019-05-23

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