CN106939824A - A kind of composite power axial and radial flowing compressor - Google Patents
A kind of composite power axial and radial flowing compressor Download PDFInfo
- Publication number
- CN106939824A CN106939824A CN201710335359.8A CN201710335359A CN106939824A CN 106939824 A CN106939824 A CN 106939824A CN 201710335359 A CN201710335359 A CN 201710335359A CN 106939824 A CN106939824 A CN 106939824A
- Authority
- CN
- China
- Prior art keywords
- compressor
- flow
- axial
- radial
- footpath
- 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
- 239000002131 composite material Substances 0.000 title claims abstract description 31
- 230000003068 static effect Effects 0.000 claims description 26
- 238000002485 combustion reaction Methods 0.000 claims description 6
- 230000001088 anti-asthma Effects 0.000 claims description 4
- 239000000924 antiasthmatic agent Substances 0.000 claims description 4
- 230000004044 response Effects 0.000 abstract description 10
- 230000008901 benefit Effects 0.000 abstract description 3
- 238000005516 engineering process Methods 0.000 description 5
- 239000002360 explosive Substances 0.000 description 2
- 230000008676 import Effects 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000001052 transient effect Effects 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000001914 calming effect Effects 0.000 description 1
- 238000009792 diffusion process Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/24—Control of the pumps by using pumps or turbines with adjustable guide vanes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
-
- 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
- F04D29/52—Casings; Connections of working fluid for axial pumps
- F04D29/54—Fluid-guiding means, e.g. diffusers
- F04D29/541—Specially 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
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/52—Casings; Connections of working fluid for axial pumps
- F04D29/54—Fluid-guiding means, e.g. diffusers
- F04D29/56—Fluid-guiding means, e.g. diffusers adjustable
- F04D29/563—Fluid-guiding means, e.g. diffusers adjustable specially 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
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses a kind of composite power axial and radial flowing compressor, the footpath flow air compressor that the axial flow compressor and one-level driven including one-level by motor is driven by turbocharger, axial flow compressor is set gradually vertically with footpath flow air compressor, axial flow compressor is connected to motor, and footpath flow air compressor is connected to the booster main shaft of turbocharger.In such a axial and radial flowing compressor, axial flow compressor is driven respectively by motor and booster main shaft successively with footpath flow air compressor, it disclosure satisfy that high pulling torque of the booster in slow-speed of revolution operating mode, the high boost presence and fast-response demand of high speed or high load capacity operating mode, the axial flow compressor control of motor driving is more flexible, can improve rotating speed, the air-flow that increase enters in the flow air compressor of footpath, two-stage supercharging can be realized in high operating mode, improve engine power density, further lift the pressure ratio of booster, advantage with compactedness, it can ensure that the booster for being equipped with the axial and radial flowing compressor meets the matching demand of the full operating condition of diesel engine.
Description
Technical field
The present invention relates to turbine and technical field of internal combustion engines, more particularly to a kind of composite power axial and radial flowing compressor.
Background technology
Internal combustion engine belongs to reciprocating power machinery, and range of operation is more broad, and the turbocharger matched with internal combustion engine
Centrifugal compressor belongs to rotating machinery, and its Effec-tive Function scope is narrower.When booster and Engine Matching are in low operating mode, start
Machine is in high operating mode, and then booster centrifugal compressor impeller exceeds the speed limit.When turbocharger and Engine Matching are in middle high operating mode,
Then boosting capability is not enough for the low operating mode of engine, and engine performance driving economy is poor, and moment of torsion is not enough, and transient response is poor, and this is turbine
The shortcoming of engine with supercharger all the time.
Thus, many new type pressurized technologies are arisen at the historic moment, and the preferable scheme of one of which is to use diameter of axle stream turbocharging
Technology.Traditional axle radial flow turbocharger is by Aerial weapon equipment technology is developed, including diameter of axle stream pressure
Mechanism of qi, i.e., add one-level axial flow compressor before radial-flow compressor, high pressure ratio be reasonably assigned to two stage compressor up, can
To be issued to expected high pressure ratio in low rim velocity, to meet the requirement of low speed torque and high operating mode high pressure ratio.However, due to this
The turbine characteristic of booster does not become, and generator terminal of calming the anger drives axial flow compressor and footpath flow air compressor by a turbine shaft, low
Operating mode transient response is poor.
Therefore, the requirement of the low-speed big, fast-response, high boost presence of the low operating mode of booster how is met, together
When ensure high operating mode high pressure ratio, be the current technical issues that need to address of those skilled in the art.
The content of the invention
In view of this, it is an object of the invention to provide a kind of composite power axial and radial flowing compressor, it disclosure satisfy that booster
The requirement of low-speed big, fast-response, while high operating mode high pressure ratio is ensure that, and it is flexible etc. with compactedness and control
Feature.
To achieve the above object, the present invention provides following technical scheme：
A kind of composite power axial and radial flowing compressor, including the axial flow compressor that is driven by motor of one-level and one-level are by turbine
The footpath flow air compressor of booster driving, the axial flow compressor is set gradually vertically with the footpath flow air compressor, the axle stream
Compressor is connected to motor, and the footpath flow air compressor is connected to the booster main shaft of the turbocharger.
Preferably, include successively vertically and towards the direction of the footpath flow air compressor in the axial flow compressor adjustable
IGV prewhirls nozzle ring, primary axis flowing leaf grating and primary axis stream static cascade, and the adjustable IGV prewhirls nozzle ring, the primary axis
Flowing leaf grating and the primary axis stream static cascade are sequentially connected, and axle flowing leaf grating is connected to the motor.
Preferably, the footpath flow air compressor includes radial-flow impeller, impeller chimney, diffuser and compressor volute, the runoff
Impeller, the diffuser, the compressor volute are radially arranged successively from inside to outside, and the impeller chimney covers at the runoff
The outside of impeller and the compressor volute is connected to, the radial-flow impeller is connected to the booster main shaft.
Preferably, the adjustable IGV prewhirls shell, the shell of the axle stream static cascade and the impeller chimney edge of stator
Axially set gradually, the adjustable IGV prewhirls to be sealed in the axial direction between the shell of stator and the shell of the axle stream static cascade
Connection, being provided between the shell and the impeller chimney of the axle stream static cascade is used for the airspace that gas passes through.
Preferably, also ring is expanded including flow, the flow, which expands ring and includes being used for being sheathed on the adjustable IGV prewhirling, leads
The connection wall of the ring-type of the outer side of leaf and the blade around circumference on the inside of the connection wall, the impeller chimney are included along footpath
To the internal ring wall and external annulus set gradually from inside to outside, and the internal ring wall is connected with the external annulus, the internal ring wall with
The airspace is formed between the shell of the axle stream static cascade, the external annulus are tightly connected with the connection wall, described
Blade, the adjustable IGV prewhirl the shell of stator, the shell of the axle stream static cascade, the internal ring wall, the external annulus, institute
State formation casing anti-asthma structure between connection wall.
Preferably, the flow expands the supporting walls that ring also includes being sheathed on the ring-type on the outside of the connection wall, the branch
Support wall is fixedly connected with the compressor volute, and the supporting walls, the compressor volute, the external annulus, the connection
The cavity for radiating is formed between wall.
In the composite power axial and radial flowing compressor that the present invention is provided, axial flow compressor is individually driven by motor, runoff pressure
Mechanism of qi is driven by booster main shaft.Air-flow between axial flow compressor and footpath flow air compressor is matched can be by the rotating speed of motor
Flexible modulation.
During the low operating mode of engine, turbocharger is short of power, and rotating speed reduction, boosting capability is weaker.Now, by electronic
Machine direct drive axial flow compressor realizes supercharging, and boost pressure is mainly derived from axial flow compressor, to meet the low operating mode of engine
The demand of boost pressure, meanwhile, motor drive shaft flow air compressor is not influenceed by engine operating condition, can improve engine quick
Response.During the high operating mode of engine, axial flow compressor realizes that one-level is pressurized by motor driving, now, and turbocharger turns
Speed is higher, drives footpath flow air compressor to realize two-stage supercharging by booster main shaft, to meet the high pressure-charging need of the high operating mode of engine
Ask.
It can be seen that, in such a composite power axial and radial flowing compressor, axial flow compressor and footpath flow air compressor successively by motor and
Booster main shaft drives acting respectively, disclosure satisfy that booster meets the low-speed big of engine, high boost presence and quick
Response demand, the axial flow compressor control of motor driving is more flexible, can improve rotating speed, increase is calmed the anger into runoff
Air-flow in machine, meanwhile, it can realize two-stage supercharging in high operating mode, improve high pressure-charging pressure required during the high operating mode of engine
Power, and the advantage with compactedness, so that it is complete to ensure that the booster for being equipped with the composite power axial and radial flowing compressor meets diesel engine
The matching demand of operating mode.
Brief description of the drawings
In order to illustrate more clearly about the embodiment of the present invention or technical scheme of the prior art, below will be to embodiment or existing
The accompanying drawing to be used needed for having technology description is briefly described, it should be apparent that, drawings in the following description are only this
The embodiment of invention, for those of ordinary skill in the art, on the premise of not paying creative work, can also basis
The accompanying drawing of offer obtains other accompanying drawings.
Fig. 1 is the axial section of composite power axial and radial flowing compressor provided by the present invention；
Fig. 2 is the explosive view of composite power axial and radial flowing compressor provided by the present invention.
In Fig. 1 and Fig. 2,1- motor, 2- is adjustable IGV prewhirls stator, 3- flows expand ring, and 31 be connection wall, and 32 be branch
Support wall, 33- blades, 4- axles flowing leaf grating, 5- axle stream static cascades, 6- radial-flow impellers, 7- impeller chimneies, 71 be internal ring wall, and 72 be outer
Ring wall, 73 be airspace, 8- diffusers, 9- compressor volutes.
Embodiment
Below in conjunction with the accompanying drawing in the embodiment of the present invention, the technical scheme in the embodiment of the present invention is carried out clear, complete
Site preparation is described, it is clear that described embodiment is only a part of embodiment of the invention, rather than whole embodiments.It is based on
Embodiment in the present invention, it is every other that those of ordinary skill in the art are obtained under the premise of creative work is not made
Embodiment, belongs to the scope of protection of the invention.
The core of the present invention is to provide a kind of composite power axial and radial flowing compressor, disclosure satisfy that the low speed of engine is big and turns round
Square, fast-response, the requirement of high boost presence, while ensure that high operating mode high pressure ratio.
Fig. 1 and Fig. 2 are refer to, Fig. 1 is the axial section of composite power axial and radial flowing compressor provided by the present invention；Fig. 2
For the explosive view of composite power axial and radial flowing compressor provided by the present invention.
In a kind of specific embodiment of composite power axial and radial flowing compressor provided by the present invention, including primary axis stream is calmed the anger
Machine, one-level footpath flow air compressor, axial flow compressor are set gradually vertically with footpath flow air compressor.Wherein, axial flow compressor is by electronic
Machine 1 drives, and axial flow compressor is connected to motor 1；Footpath flow air compressor is driven by turbocharger, and footpath flow air compressor is connected to increasing
Depressor main shaft.Such a composite power axial and radial flowing compressor can be used for supercharging of internal combustion engine in the booster of internal combustion engine.Wherein, axle
The central rotating shaft of the central rotating shaft of flow air compressor and footpath flow air compressor can collinearly be set.Axial flow compressor and footpath flow air compressor it
Between air-flow matching can be by the rotating speed flexible modulation of motor 1.
It should be noted that axial, circumference herein, radially on the basis of the booster main shaft of turbocharger, increase
The bearing of trend of depressor main shaft is axial direction.
During the low operating mode of engine, turbocharger is short of power, and runoff rotating speed of gas compressor reduction, boosting capability is weaker, this
When, axial flow compressor is directly driven by motor 1 and realizes supercharging, boost pressure is mainly derived from axial flow compressor, to meet
The demand of the low operating mode boost pressure of engine, meanwhile, the driving axial flow compressor of motor 1 is not influenceed by engine operating condition, can be with
Improve engine fast-response.During the high operating mode of engine, axial flow compressor realizes that one-level is pressurized by the driving of motor 1, this
When, turbo charger speed is higher, drives footpath flow air compressor to realize two-stage supercharging by booster main shaft, high to meet engine
The high pressure-charging demand of operating mode.
It can be seen that, in such a composite power axial and radial flowing compressor, axial flow compressor and footpath flow air compressor successively by motor 1 and
Booster main shaft drives respectively, disclosure satisfy that the low-speed big, high boost presence and fast-response demand of engine, electronic
The axial flow compressor control that machine 1 drives is more flexible, can improve rotating speed, the air-flow that increase enters in the flow air compressor of footpath, together
When, it can realize two-stage supercharging in high operating mode, improve high boost presence required during the high operating mode of engine, and with compactedness
Advantage, so as to ensure that the booster for being equipped with the composite power axial and radial flowing compressor meets the matching demand of diesel engine full working scope.
Specifically, in axial flow compressor vertically and towards the direction of footpath flow air compressor can successively include adjustable IGV it is pre-
Revolve nozzle ring 2, primary axis flowing leaf grating 4 and primary axis stream static cascade 5, adjustable IGV prewhirls nozzle ring 2, primary axis flowing leaf grating 4
It is sequentially connected with primary axis stream static cascade 5, and axle flowing leaf grating 4 is connected to motor 1, axle flowing leaf grating 4 is independent by motor 1
Drive.
During work, air is inhaled into axle flowing leaf grating 4 through adjustable IGV stators 2 of prewhirling, and axle flows leaf grating 4 by mechanical energy
Pressure energy and kinetic energy are converted into, after air compresses through axial flow compressor, is flowed into the flow air compressor of footpath.
Wherein, adjustable IGV prewhirls stator 2 at the import of axial flow compressor, and the prewhirl stators of stator 2 of adjustable IGV are opened
Degree can be adjusted, and the regulation in charge air flow direction can be carried out at the import of axial flow compressor, can expand compressor operation
Scope, is conducive to avoiding surge and the appearance of clogging.
Specifically, footpath flow air compressor can include radial-flow impeller 6, impeller chimney 7, diffuser 8 and compressor volute 9, runoff
Impeller 6, diffuser 8, compressor volute 9 are radially arranged successively from inside to outside, and impeller chimney 7 covers at the outside of radial-flow impeller 6
And compressor volute 9 is connected to, radial-flow impeller 6 is connected to booster main shaft.Wherein, diffuser 8 is specifically as follows blade diffusion
Device can also be vaneless diffuser.
During work, gas flow through successively motor 1, adjustable IGV prewhirl stator 2, axle flowing leaf grating 4, axle stream static cascade 5,
Radial-flow impeller 6, diffuser 8, compressor volute 9, are then fed into engine, the footpath flow air compressor can turbocharger drive
Dynamic lower reliable operation.
Specifically, adjustable IGV prewhirl shell, the shell of axle stream static cascade 5 and the impeller chimney 7 of stator 2 can be vertically
Set gradually, the prewhirl shells of shell and axle stream static cascade 5 of stator 2 of adjustable IGV are tightly connected in the axial direction, axle stream static cascade
Can be provided between 5 shell and impeller chimney 7 is used for the airspace 73 that gas passes through.When rotating speed of gas compressor is reduced, air-flow
It can be exported from the airspace 73, increase the air inflow of impeller inlet, so as to widen stall margin.Wherein, pass through
Adjustable IGV is prewhirled the setting of the axial length of the shell of stator 2, axle can be made to flow leaf grating 4 and also be located at adjustable IGV and prewhirl to lead
The enclosure of leaf 2.
Further, adjustable IGV prewhirl stator 2 shell and the shell of axle stream static cascade 5 between can be fixedly connected, with
Just the stable installation of axle stream static cascade 5 is ensured.
On the basis of each above-mentioned embodiment, the composite power axial and radial flowing compressor can also include flow and expand ring 3,
Flow expand ring 3 specifically include for be set in adjustable IGV prewhirl stator 2 shell outside connection wall 31 and set around circumferential
Put the blade in the inner side of connection wall 31, connection wall 31 is annular in shape, i.e., blade be arranged on adjustable IGV prewhirl stator 2 shell with
Between connection wall 31.Impeller chimney 7 includes the internal ring wall 71 and external annulus 72 radially set gradually from inside to outside, and internal ring wall 71
It is connected with external annulus 72, internal ring wall 71 specifically can be connected to form groove with external annulus 72.Internal ring wall 71 and axle stream static cascade 5
Airspace 73 is formed between shell, external annulus 72 are tightly connected with connection wall 31.Blade, adjustable IGV prewhirl the outer of stator 2
Casing anti-asthma structure is formed between shell, the shell of axle stream static cascade 5, internal ring wall 71, external annulus 72 and connection wall 31.
When composite power axial and radial flowing compressor is in big flow operating mode, a part of gas can prewhirl into adjustable IGV
Annular space (i.e. machine between shell, the shell of axle stream static cascade 5, internal ring wall 71, external annulus 72 and the connection wall 31 of stator 2
Casket anti-asthma structure) in, and by the additional-air inlet of airspace 73, the flow in composite power axial and radial flowing compressor can have a small amount of expansion
Greatly；When composite power axial and radial flowing compressor is in low flow rate condition, the air into axial and radial flowing compressor tails off, radial-flow impeller
The separation enhancing of 6 internal gas flows, air can flow backwards under the inside adverse pressure gradient effect of radial-flow impeller 6, and now, air-flow can be from ventilation
Flow out, and flowed out from above-mentioned annular space in gap 73, so as to increase the air inflow of impeller inlet to a certain extent, improved
Radial-flow impeller analyzes phenomenon, so as to expand stall margin.
Further, flow expands the supporting walls 32 that ring 3 can also include being sheathed on the outside of connection wall 31, supporting walls 32
Annularly, supporting walls 32 are fixedly connected with compressor volute 9, and supporting walls 32, compressor volute 9, external annulus 72, connection wall 31
Between form the cavity for radiating.Supporting walls 32 are connected to compressor volute 9, and the connection that can improve flow expansion ring 3 is strong
Degree, while the bulk strength of the composite power axial and radial flowing compressor is improved, meanwhile, the setting of the cavity can increase composite power
The contact area of axial and radial flowing compressor and air, is conducive to radiating.
The embodiment of each in this specification is described by the way of progressive, and what each embodiment was stressed is and other
Between the difference of embodiment, each embodiment identical similar portion mutually referring to.
Composite power axial and radial flowing compressor provided by the present invention is described in detail above.Tool used herein
Body example is set forth to the principle and embodiment of the present invention, and the explanation of above example is only intended to help and understands this hair
Bright method and its core concept.It should be pointed out that for those skilled in the art, not departing from the present invention
On the premise of principle, some improvement and modification can also be carried out to the present invention, these are improved and modification also falls into right of the present invention
It is required that protection domain in.
Claims (6)
1. a kind of composite power axial and radial flowing compressor, for supercharging of internal combustion engine, it is characterised in that driven including one-level by motor
Axial flow compressor and the footpath flow air compressor that is driven by turbocharger of one-level, the axial flow compressor and the footpath flow air compressor
Set gradually vertically, the axial flow compressor is connected to motor (1), the footpath flow air compressor is connected to the turbocharging
The booster main shaft of device.
2. composite power axial and radial flowing compressor according to claim 1, it is characterised in that along axle in the axial flow compressor
To and towards the footpath flow air compressor direction successively including adjustable IGV prewhirl nozzle ring (2), primary axis flowing leaf grating (4) and
Primary axis stream static cascade (5), the adjustable IGV prewhirls nozzle ring (2), primary axis flowing leaf grating (4) and the primary axis
Stream static cascade (5) is sequentially connected, and axle flowing leaf grating (4) is connected to the motor (1).
3. composite power axial and radial flowing compressor according to claim 2, it is characterised in that the footpath flow air compressor includes footpath
Flow impeller (6), impeller chimney (7), diffuser (8) and compressor volute (9), the radial-flow impeller (6), the diffuser (8), institute
State compressor volute (9) to be radially arranged successively from inside to outside, the impeller chimney (7) covers at the outer of the radial-flow impeller (6)
Side and the compressor volute (9) is connected to, the radial-flow impeller (6) is connected to the booster main shaft.
4. composite power axial and radial flowing compressor according to claim 3, it is characterised in that the adjustable IGV prewhirls stator
(2) shell, the shell of the axle stream static cascade (5) and the impeller chimney (7) is set gradually vertically, the adjustable IGV
Prewhirl and be tightly connected in the axial direction between the shell of stator (2) and the shell of the axle stream static cascade (5), the axle stream static cascade
(5) being provided between shell and the impeller chimney (7) is used for the airspace (73) that gas passes through.
5. composite power axial and radial flowing compressor according to claim 4, it is characterised in that also expand ring (3) including flow,
The flow expand ring (3) include being used for being sheathed on the adjustable IGV prewhirl stator (2) outer side ring-type connection wall
(31) and around the circumferential blade (33) on the inside of the connection wall (31), the impeller chimney (7) is included radially from inside to outside
The internal ring wall (71) and external annulus (72) set gradually, and the internal ring wall (71) is connected with the external annulus (72), it is described in
The airspace (73), the external annulus (72) and institute are formed between ring wall (71) and the shell of the axle stream static cascade (5)
State connection wall (31) to be tightly connected, the blade (33), the adjustable IGV are prewhirled the shells of stator (2), the axle stream static cascade
(5) casing anti-asthma structure is formed between shell, the internal ring wall (71), the external annulus (72), the connection wall (31).
6. composite power axial and radial flowing compressor according to claim 5, it is characterised in that the flow expands ring (3) also
Including the supporting walls (32) for the ring-type being sheathed on the outside of the connection wall (31), the supporting walls (32) and the compressor volute
(9) it is fixedly connected, and the supporting walls (32), the compressor volute (9), the external annulus (72), the connection wall (31)
Between form the cavity for radiating.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710335359.8A CN106939824A (en) | 2017-05-11 | 2017-05-11 | A kind of composite power axial and radial flowing compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710335359.8A CN106939824A (en) | 2017-05-11 | 2017-05-11 | A kind of composite power axial and radial flowing compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106939824A true CN106939824A (en) | 2017-07-11 |
Family
ID=59464894
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710335359.8A Pending CN106939824A (en) | 2017-05-11 | 2017-05-11 | A kind of composite power axial and radial flowing compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106939824A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112012962A (en) * | 2020-08-05 | 2020-12-01 | 合肥工业大学 | Double-rotor turbocharger |
| CN112697384A (en) * | 2020-12-24 | 2021-04-23 | 中国人民解放军国防科技大学 | Large-flow high-pressure air continuous production system |
| CN113389741A (en) * | 2021-07-29 | 2021-09-14 | 深圳飞磁科技有限公司 | Two-stage high-speed air suspension centrifugal blower turbine device |
| CN114370433A (en) * | 2021-12-20 | 2022-04-19 | 中国北方发动机研究所(天津) | Compressor with variable air inlet prerotation generator |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5025629A (en) * | 1989-03-20 | 1991-06-25 | Woollenweber William E | High pressure ratio turbocharger |
| CN101922459A (en) * | 2010-07-28 | 2010-12-22 | 寿光市康跃增压器有限公司 | Electric composite multi-stage centrifugal compressor device |
| CN203756317U (en) * | 2014-04-14 | 2014-08-06 | 大连交通大学 | Air intake device applicable to supercharger |
| CN204200674U (en) * | 2014-06-27 | 2015-03-11 | 哈尔滨工程大学 | The centrifugal-flow compressor casing bleed recirculation structure of variable geometry |
| DE102015205676A1 (en) * | 2014-07-03 | 2016-01-07 | Ford Global Technologies, Llc | Supercharged internal combustion engine with exhaust gas turbocharger and auxiliary compressor and method for operating such an internal combustion engine |
| CN105465047A (en) * | 2015-12-14 | 2016-04-06 | 中国北方发动机研究所(天津) | Casing treatment device for reducing stalling and surging of air compressor |
| CN105658930A (en) * | 2013-10-24 | 2016-06-08 | 博格华纳公司 | Axial compressor with a magnetic stepper or servo motor |
| US20160195109A1 (en) * | 2013-08-09 | 2016-07-07 | Aeristech Limited | Attachment arrangement for turbo compressor |
| CN207048858U (en) * | 2017-05-11 | 2018-02-27 | 大连依勒斯涡轮增压技术有限公司 | A kind of composite power axial and radial flowing compressor |
-
2017
- 2017-05-11 CN CN201710335359.8A patent/CN106939824A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5025629A (en) * | 1989-03-20 | 1991-06-25 | Woollenweber William E | High pressure ratio turbocharger |
| CN101922459A (en) * | 2010-07-28 | 2010-12-22 | 寿光市康跃增压器有限公司 | Electric composite multi-stage centrifugal compressor device |
| US20160195109A1 (en) * | 2013-08-09 | 2016-07-07 | Aeristech Limited | Attachment arrangement for turbo compressor |
| CN105658930A (en) * | 2013-10-24 | 2016-06-08 | 博格华纳公司 | Axial compressor with a magnetic stepper or servo motor |
| CN203756317U (en) * | 2014-04-14 | 2014-08-06 | 大连交通大学 | Air intake device applicable to supercharger |
| CN204200674U (en) * | 2014-06-27 | 2015-03-11 | 哈尔滨工程大学 | The centrifugal-flow compressor casing bleed recirculation structure of variable geometry |
| DE102015205676A1 (en) * | 2014-07-03 | 2016-01-07 | Ford Global Technologies, Llc | Supercharged internal combustion engine with exhaust gas turbocharger and auxiliary compressor and method for operating such an internal combustion engine |
| CN105465047A (en) * | 2015-12-14 | 2016-04-06 | 中国北方发动机研究所(天津) | Casing treatment device for reducing stalling and surging of air compressor |
| CN207048858U (en) * | 2017-05-11 | 2018-02-27 | 大连依勒斯涡轮增压技术有限公司 | A kind of composite power axial and radial flowing compressor |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112012962A (en) * | 2020-08-05 | 2020-12-01 | 合肥工业大学 | Double-rotor turbocharger |
| CN112697384A (en) * | 2020-12-24 | 2021-04-23 | 中国人民解放军国防科技大学 | Large-flow high-pressure air continuous production system |
| CN113389741A (en) * | 2021-07-29 | 2021-09-14 | 深圳飞磁科技有限公司 | Two-stage high-speed air suspension centrifugal blower turbine device |
| CN114370433A (en) * | 2021-12-20 | 2022-04-19 | 中国北方发动机研究所(天津) | Compressor with variable air inlet prerotation generator |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US7571607B2 (en) | Two-shaft turbocharger | |
| CN106939824A (en) | A kind of composite power axial and radial flowing compressor | |
| CN104421199B (en) | The asymmetrical bilateral turbo-charger impeller of function and diffuser | |
| EP3249234A1 (en) | Turbocharger with two-stage series compressor driven by exhaust gas-driven turbine and electric motor | |
| CN207048858U (en) | A kind of composite power axial and radial flowing compressor | |
| CN103403298B (en) | Turbine wheel, turbo machine and use thereof | |
| US20170002727A1 (en) | Multi-stage electric centrifugal compressor and supercharging system for internal combustion engine | |
| US20040020203A1 (en) | High-pressure ratio turbocharger | |
| US20100104424A1 (en) | Variable turbine geometry turbocharger | |
| US20160024999A1 (en) | Turbine housing with dividing vanes in volute | |
| CN102661180A (en) | Dual-zone turbine for turbocharging | |
| US8480351B2 (en) | Compressor unit | |
| US8067844B2 (en) | Engine generator set | |
| US20160252095A1 (en) | Axial compressor with a magnetic stepper or servo motor | |
| CN105298633A (en) | Adjustable type exhaust gas turbocharger | |
| US20040237523A1 (en) | High-pressure ratio turbocharger | |
| CN103195750A (en) | Efficient gas compressor vane wheel | |
| CN107676305A (en) | A kind of stepped guide vane vaned diffuser structure | |
| CN105298921B (en) | U-shaped mixing diffuser between two-stage centrifugal compressor stage | |
| US9915199B2 (en) | Bi-directional compression fan rotor for a gas turbine engine | |
| CN208138040U (en) | The turbocharger of having electronic quick start combination unit | |
| CN208040518U (en) | Having electronic quickly starts the turbocharger of separate structure | |
| CN207539072U (en) | A kind of turbocharger rotor axis | |
| CN1400399A (en) | Small-type radial-flow or mixed-flow turbo supercharger | |
| CN108561222A (en) | Having electronic quickly starts the turbocharger of separate structure |
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 | ||
| AD01 | Patent right deemed abandoned | ||
| AD01 | Patent right deemed abandoned |
Effective date of abandoning: 20230609 |