CN109812453A - Centrifugal compressor - Google Patents
Centrifugal compressor Download PDFInfo
- 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
Links
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
Landscapes
- 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
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. a kind of centrifugal compressor (10), the especially centrifugal compressor of exhaust-driven turbo-charger exhaust-gas turbo charger,
With rotary blade (11),
With fixed shell (13),
With the primary flow channel (14) limited by the shell (13), for supplying on the direction of the impeller (11) wait press
The medium of contracting,
With the secondary flow chamber (15) for being arranged in the primary flow channel (14) radial outside, the secondary flow chamber (15) by
Contoured wall (16) defines the boundary with the primary flow channel (14), and the secondary flow chamber (15) is in the impeller (11)
Region in via secondary flow opening (18) be connected to the primary flow channel (14),
It is characterized in that,
Seen in meridional section, the secondary flow chamber (15) is connected in the region of the impeller (11) via it described
The secondary flow opening (18) of primary flow channel (14) is relative to radial direction by oblique or obliquely set.
2. centrifugal compressor according to claim 1, which is characterized in that seen in meridional section, the secondary flow
Chamber (15) is open in the region of the impeller (11) via its described secondary flow for being connected to the primary flow channel (14)
(18) include angle with the radial direction between 10 ° and 80 °.
3. centrifugal compressor according to claim 2, which is characterized in that seen in meridional section, the secondary flow
Opening (18) includes the angle with the radial direction between 10 ° and 70 °.
4. centrifugal compressor according to claim 3, which is characterized in that seen in meridional section, the secondary flow
Opening (18) includes the angle with the radial direction between 20 ° and 70 °.
5. centrifugal compressor according to claim 4, which is characterized in that seen in meridional section, the secondary flow
Opening (18) includes the angle with the radial direction between 20 ° and 60 °.
6. centrifugal compressor according to any one of claims 1 to 5, which is characterized in that in medium to be compressed
Flow direction on it is seen, the secondary flow chamber (15) is via another secondary flow opening (17) in the impeller (11) upstream
It is connected to the primary flow channel (14).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102017127421.9A DE102017127421A1 (en) | 2017-11-21 | 2017-11-21 | centrifugal compressors |
| DE102017127421.9 | 2017-11-21 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN109812453A true CN109812453A (en) | 2019-05-28 |
Family
ID=66336034
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811391436.2A Pending CN109812453A (en) | 2017-11-21 | 2018-11-21 | Centrifugal compressor |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20190154041A1 (en) |
| JP (1) | JP2019094897A (en) |
| KR (1) | KR20190058324A (en) |
| CN (1) | CN109812453A (en) |
| CH (1) | CH714389B1 (en) |
| DE (1) | DE102017127421A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102018211119A1 (en) * | 2018-07-05 | 2020-01-09 | Audi Ag | Drive device with an exhaust gas turbocharger |
| JP7220097B2 (en) | 2019-02-27 | 2023-02-09 | 三菱重工業株式会社 | Centrifugal compressor and turbocharger |
Citations (5)
| 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***有限公司 | Compressor stabilizer |
| CN103703219A (en) * | 2011-07-20 | 2014-04-02 | Ihi供应***国际有限责任公司 | Turbine for an exhaust-gas turbocharger |
| 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 |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| IT1392215B1 (en) | 2008-12-03 | 2012-02-22 | Idromeccanica Bertolini S P A | HEAD FOR PUMPS AND PROCEDURE FOR THE IMPLEMENTATION OF THAT HEAD |
| JP5479021B2 (en) * | 2009-10-16 | 2014-04-23 | 三菱重工業株式会社 | Exhaust turbocharger compressor |
| DE112014005032T5 (en) * | 2013-12-06 | 2016-08-11 | Borgwarner Inc. | Compressor air return with reduced noise |
| JP6497183B2 (en) * | 2014-07-16 | 2019-04-10 | トヨタ自動車株式会社 | Centrifugal compressor |
| WO2016151689A1 (en) * | 2015-03-20 | 2016-09-29 | 三菱重工業株式会社 | Centrifugal compressor and supercharger comprising same |
| US9951793B2 (en) * | 2016-06-01 | 2018-04-24 | Borgwarner Inc. | Ported shroud geometry to reduce blade-pass noise |
| US10316859B2 (en) * | 2017-05-12 | 2019-06-11 | Borgwarner Inc. | Turbocharger having improved ported shroud compressor housing |
| US10935035B2 (en) * | 2017-10-26 | 2021-03-02 | Hanwha Power Systems Co., Ltd | Closed impeller with self-recirculation casing treatment |
-
2017
- 2017-11-21 DE DE102017127421.9A patent/DE102017127421A1/en active Pending
-
2018
- 2018-10-18 CH CH01272/18A patent/CH714389B1/en unknown
- 2018-11-14 US US16/191,067 patent/US20190154041A1/en not_active Abandoned
- 2018-11-19 KR KR1020180142426A patent/KR20190058324A/en unknown
- 2018-11-20 JP JP2018217212A patent/JP2019094897A/en active Pending
- 2018-11-21 CN CN201811391436.2A patent/CN109812453A/en active Pending
Patent Citations (5)
| 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***有限公司 | Compressor stabilizer |
| CN103703219A (en) * | 2011-07-20 | 2014-04-02 | Ihi供应***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 |
|---|---|
| DE102017127421A1 (en) | 2019-05-23 |
| CH714389A2 (en) | 2019-05-31 |
| JP2019094897A (en) | 2019-06-20 |
| KR20190058324A (en) | 2019-05-29 |
| CH714389B1 (en) | 2021-12-15 |
| US20190154041A1 (en) | 2019-05-23 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WD01 | Invention patent application deemed withdrawn after publication | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20190528 |