CN102840169A - Centrifugal compressor used for generating two different pressure ratios - Google Patents
Centrifugal compressor used for generating two different pressure ratios Download PDFInfo
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- CN102840169A CN102840169A CN2012103653208A CN201210365320A CN102840169A CN 102840169 A CN102840169 A CN 102840169A CN 2012103653208 A CN2012103653208 A CN 2012103653208A CN 201210365320 A CN201210365320 A CN 201210365320A CN 102840169 A CN102840169 A CN 102840169A
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Abstract
The invention relates to a centrifugal compressor used for generating two different pressure ratios. The centrifugal compressor belongs to the technical field of a supercharging of an internal combustion engine and comprises a front shell of a compressor, a rear shell of the compressor, an annular splitter plate and step-shaped centrifugal compressor impellers. A compressor air inlet and a compressor front air collecting runner volute are arranged on the front shell of the compressor, a compressor back air collecting runner volute is arranged on the rear shell of the compressor; the compressor front air collecting runner volute is connected with the compressor back air collecting runner volute by adopting a bolt, and the annular splitter plate is arranged between the compressor front air collecting runner volute and the compressor back air collecting runner volute; a pressure enlarging passage consisting of the compressor front air collecting runner volute and the compressor back air collecting runner volute is divided into two parts by the annular splitter plate, thereby forming a dual-runner vaneless diffuser; step shaped centrifugal compressor impellers are arranged at the inner parts of the front shell of the compressor and the rear shell of the compressor; the outlets of the impellers are provided with big and small diameters, so that the outlets of the impeller are formed to be in a ladder shape. By using one compressor, two compressed airs with different pressure ratios is generated; the centrifugal compressor is applicable to the condition required to generate the compressed air with two pressure ratios simultaneously.
Description
Technical field
Invention relates to the compressor apparatus of a kind of internal-combustion engine with turbosupercharger, and particularly a kind of centrifugal compressor device that is used to produce two kinds of different pressure ratios belongs to the supercharging of internal combustion engine technical field.
Background technique
At present, the pressurized machine that most of vehicle internal combustion engine mated is the ordinary single-stage turbosupercharger.When automobile went on the Plain, the pressure ratio that single-stage supercharger produced generally can reach the coupling requirement of internal-combustion engine.Yet; When automobile gets into the plateau; Receive the restriction of pressurized machine pressure ratio, rotating speed and range of flow, phenomenons such as air-intake of combustion engine quantity not sufficient, power decline, supercharger speed rising, operation point entering nonclient area can occur, single-stage supercharger often can not adapt to the plateau bad working environment.This just needs to introduce a kind of high-pressure system, the working state when the two-stage supercharging system can make internal-combustion engine under altitude environment, return to the Plain as a kind of high-pressure system with the obvious advantage.But this pressurization system structurally need be arranged two pressurized machines; Not only increased the difficulty of confined space inner piece compact Layout; And travel on the plains region or only need single-stage supercharger just can satisfy the situation of supercharging of internal combustion engine requirement for the most of the time, increased the complexity of internal combustion engine operation undoubtedly.
Miniature gas turbine more and more received people's attention in recent years as a kind of auxiliary power unit, and miniature gas turbine is applied to the two-stage supercharging system, can make the low pressure stage gas compressor of gas turbine drives additional mechanical supercharging gas compressor as the two-stage supercharging system.Publication number is a kind of additional mechanical supercharging system for the patent of " Cn102155290 " relates to; As shown in Figure 1; Internal combustion engine is when the low altitude area; Switching valve 9 only makes atmosphere be communicated with empty filter 10, relies on main pressurization system (dashed region among Fig. 1) and internal-combustion engine 13 normal coupling and work, and its working principle and common boosting internal combustion engine are as good as.When internal combustion engine during in the high altitude localities; Adopt high-pressure air to supply with firing chamber 6 across-the-line starting additional mechanical supercharging systems, fresh air at first through behind the auxiliary empty filter 1, gets into additional mechanical supercharging gas compressor 2 and auxiliary combustion gas compressor 3 respectively; After overcompression, air temperature and pressure are improved.Fuel oil is injected in the firing chamber 6 through solenoid valve fueling injection equipment 5; The fuel oil of process atomizing mixes with the pressurized air from auxiliary combustion gas compressor 3; By firing chamber ignition mechanism 7 gas mixture is lighted; The high-temperature fuel gas that produces promotes auxiliary turbine 4 expansion actings, and to drive additional mechanical supercharging gas compressor 2 and auxiliary combustion gas compressor 3, control system 8 is regulated the working condition of additional mechanical supercharging system according to boost pressure.The pressurized air that is flowed out by additional mechanical supercharging gas compressor 2 is flowed through behind switching valve 9 and the empty filter 10, enters into gas compressor 11 by further compression, and temperature and pressure continues to improve, and then through intercooler 12 coolings, reduces the temperature and the volume flowrate of air.After the such pressurization of process, air gets into internal-combustion engine 13 and fuel oil mixed combustion, and the high-temp waste gas of the generation of burning enters into the turbine 14 expansion actings of main pressurization system, to drive its gas compressor 11, enters atmosphere through the waste gas after turbine 14 expansions.
Because auxiliary turbine 4 actings not only will drive auxiliary combustion gas compressor 3, also will drive additional mechanical supercharging gas compressor 2, formed the structural type of a turbine and two gas compressor series connection.This form makes that whole rotor-support-foundation system is long; Thereby increased rotor disequilibrium, the flex resistance of rotor-support-foundation system and rigidity have been proposed high requirement, have increased wearing and tearing and reduced mechanical efficiency; So need improve this kind structural type, two gas compressors are united two into one.Yet the required pressure ratio of auxiliary combustion gas compressor is generally more than 3.0, and is generally 1.3～2.0 as the required pressure ratio of the additional mechanical supercharging gas compressor of rudimentary gas compressor in the two-stage supercharger.Therefore, need a kind of centrifugal compressor of taking into account auxiliary combustion gas compressor and additional mechanical supercharging gas compressor function of design.
Summary of the invention
In view of this, the invention provides a kind of centrifugal compressor that is used to produce two kinds of different pressure ratios, both satisfied the pressure ratio requirement of auxiliary combustion gas compressor, also satisfy the pressure ratio requirement of additional mechanical supercharging gas compressor simultaneously.
To achieve these goals, the technological scheme that the present invention adopted is:
A kind of centrifugal compressor that is used to produce two kinds of different pressure ratios comprises gas compressor fore shell, gas compressor back cover, annular slab and stepped centrifugal compressor impeller; Wherein, wherein, the gas compressor fore shell is provided with compressor air inlet machine mouth and the preceding gas collection runner spiral case of gas compressor; The gas compressor back cover is provided with gas collection runner spiral case behind the gas compressor; Before the gas compressor behind gas collection runner spiral case and the gas compressor gas collection runner spiral case be fixedly connected; And clamping annular slab between its connection part, the part outside the annular slab clamp face are annular flow distribution plate, at gas compressor fore shell and gas compressor back cover inside stepped centrifugal compressor impeller are installed; It is stepped that stepped centrifugal compressor impeller outlet makes the impeller outlet place form two-stage; One side plane of annular flow distribution plate is corresponding to the step surface position of stepped centrifugal compressor impeller outlet two-stage step, and annular flow distribution plate and step surface leave the gap, and this gap does not influence the rotation of stepped centrifugal compressor impeller; The annular flow distribution plate is divided into two the diffusion passage of gas compressor fore shell diffusion wall and gas compressor back cover diffusion wall composition; Near gas compressor fore shell end be preceding vaneless diffuser, near gas compressor back cover end be the back vaneless diffuser, preceding vaneless diffuser with the back vaneless diffuser form the double flow channel vaneless diffuser jointly.
Gas collection runner spiral case exterior boss is provided with the fore shell bolt hole before the gas compressor of said gas compressor fore shell.
Gas collection runner spiral case exterior boss is provided with the back cover bolt hole behind the gas compressor of said gas compressor back cover, and the back cover bolt hole is corresponding with fore shell bolt hole on the gas compressor fore shell boss, and inserting bolt is connected the gas compressor fore shell and tightens together with the gas compressor back cover.
Be processed with annular boss and the annular groove that cooperatively interacts on the junction surface of said gas compressor fore shell and gas compressor back cover respectively, be beneficial to the installing and locating of gas compressor fore shell and gas compressor back cover.
Said annular slab surface Machining has along the radially stiffening rib that circumferentially is uniformly distributed with, and is used to increase its intensity and rigidity;
As a kind of technological scheme; Said stepped centrifugal compressor impeller outlet is designed to minor diameter near gas compressor fore shell end; Be designed to major diameter near gas compressor back cover end; As another kind of technological scheme, said stepped centrifugal compressor impeller outlet is designed to major diameter near gas compressor fore shell end, is designed to minor diameter near gas compressor back cover end.
Two runners of said double flow channel vaneless diffuser are collected two strands of gases that pressure is different that produced by stepped centrifugal compressor impeller respectively.
Beneficial effect:
1, the present invention utilizes stepped centrifugal compressor impeller to make a gas compressor produce the pressurized air of two kinds of different pressure ratios; Taken into account the function of auxiliary combustion gas compressor and additional mechanical supercharging gas compressor; Two gas compressors in the system are united two into one; Overall structure obtains simplifying, and has improved balancing rotor property simultaneously, reduced requirement, the wearing and tearing of reduction system mechanics to rotor-support-foundation system flex resistance and rigidity and has improved mechanical efficiency.
2, the present invention also can be applicable to other and need produce under two kinds of compressed-air actuated situation of pressure ratio.
Description of drawings
Fig. 1 recovers the high motive combustion type additional mechanical supercharging system schematic of internal-combustion engine being used in the background technique of the present invention.
Fig. 2 is the structural representation that being used in the embodiment of the invention 1 produces the centrifugal compressor device of two kinds of different pressure ratios.
Fig. 3 is the structural representation of the annular slab among the present invention.
Fig. 4 is the stepped centrifugal compressor impeller structural representation in the embodiment of the invention 1.
Fig. 5 is the structural representation that being used in the embodiment of the invention 2 produces the centrifugal compressor device of two kinds of different pressure ratios.
Fig. 6 is the stepped centrifugal compressor impeller structural representation in the embodiment of the invention 2.
Among the figure: 1-assists empty filter; 2-additional mechanical supercharging gas compressor; 3-auxiliary combustion gas compressor; 4-assists turbine; 5-solenoid valve fueling injection equipment; The 6-firing chamber; The 7-ignition mechanism; 8-starting and control system; The 9-switching valve; The empty filter of 10-; The 11-gas compressor; The 12-intercooler; The 13-internal-combustion engine; The 14-turbine; 15-gas compressor fore shell; Gas collection runner spiral case before the 16-gas compressor; 17-annular flow distribution plate; 18-gas compressor fore shell diffusion wall; 19-minor diameter impeller outlet front end; 20-compressor air inlet machine mouth; The stepped centrifugal compressor impeller of 21-; Vaneless diffuser before the 22-; 23-gas compressor back cover; Gas collection runner spiral case behind the 24-gas compressor; 25-double flow channel vaneless diffuser; 26-gas compressor back cover diffusion wall; 27-major diameter impeller outlet rear end; The 28-impeller outlet; Vaneless diffuser behind the 29-; 30-fore shell bolt hole; 31-back cover bolt hole; The 33-stiffening rib; 34-annular flow distribution plate; 35-major diameter impeller outlet front end; 36-minor diameter impeller outlet rear end.
Embodiment
Below in conjunction with the accompanying drawing embodiment that develops simultaneously, describe the present invention.
Embodiment 1: as shown in Figure 2, a kind of centrifugal compressor device that is used to produce two kinds of different pressure ratios comprises gas compressor fore shell 15, gas compressor back cover 23, annular slab 17 and stepped centrifugal compressor impeller 21.Gas compressor fore shell 15 is provided with compressor air inlet machine mouth 20 and the preceding gas collection runner spiral case 16 of gas compressor; Gas compressor back cover 23 is provided with gas collection runner spiral case 24 behind the gas compressor, and gas compressor fore shell 15 adopts bolts to be connected with gas compressor back cover 23, and clamping has annular slab 17 therebetween, and annular slab 17 clamp faces part in addition is annular flow distribution plate 34; The diffusion passage that annular flow distribution plate 34 is formed gas compressor fore shell diffusion wall 18 and gas compressor back cover diffusion wall 26 is divided into two, and has formed double flow channel vaneless diffuser 25; In gas compressor fore shell 15 and gas compressor back cover 23 inside stepped centrifugal compressor impeller 21 is installed, impeller outlet 28 is stepped for two kinds of diameters of size form the impeller outlet place.
Said gas compressor fore shell 15 is provided with compressor air inlet machine mouth 20 and the preceding gas collection runner spiral case 16 of gas compressor, on the spiral case exterior boss, is provided with fore shell bolt hole 30.
Said gas compressor back cover 23 is provided with gas collection runner spiral case 24 behind the gas compressor; On the spiral case exterior boss, be provided with back cover bolt hole 31; Back cover bolt hole 31 is corresponding with fore shell bolt hole 30 on the gas compressor fore shell boss, and inserting bolt is connected gas compressor fore shell 15 and tightens together with gas compressor back cover 23.
Be processed with annular boss and the annular groove that cooperatively interacts respectively on the junction surface of said gas compressor fore shell 15 and gas compressor back cover 23,
As shown in Figure 3, said annular slab 17 surface Machining have along the radially stiffening rib 33 that circumferentially is uniformly distributed with, and are used to increase its intensity and rigidity.Annular slab 17 is clamped in before the gas compressor behind the gas collection runner spiral case 16 and gas compressor between the gas collection runner spiral case 24; The diffusion passage that annular flow distribution plate 34 is formed gas compressor fore shell diffusion wall 18 and gas compressor back cover diffusion wall 26 is divided into two; Near gas compressor fore shell 15 ends is preceding vaneless diffuser 22; Near gas compressor back cover 22 ends be back vaneless diffuser 29, preceding vaneless diffuser 22 has formed double flow channel vaneless diffuser 25 with back vaneless diffuser 29.
Two runners of said double flow channel vaneless diffuser 25 are collected two strands of gases that pressure is different that produced by stepped centrifugal compressor impeller 21 respectively.
As shown in Figure 4; Said stepped centrifugal compressor impeller 21; Its impeller outlet 28 constitutes step structure by minor diameter impeller outlet front end 19 and major diameter impeller outlet rear end 27, and impeller outlet 28 is designed to minor diameter near gas compressor fore shell end, is designed to major diameter near gas compressor back cover end.
After air gets into gas compressor by compressor inlet 20; Flow into stepped centrifugal compressor impeller 21 parts of gas compressor along inlet channel; Stepped centrifugal compressor impeller 21 and rotor thereof carry out rotation motion owing to driven by turbine or other power equipments, and air-flow is and then made high speed rotating under the drive of stepped centrifugal compressor impeller 21 blades.Gas is owing to receive the effect of rotary centrifugal force, and flows at the diffusion of 21 li of stepped centrifugal compressor impellers, and gas pressure in stepped centrifugal compressor impeller 21 is improved gradually.Part air communication is crossed the preceding vaneless diffuser 22 that minor diameter impeller outlet front end 19 gets near gas compressor fore shell 15 ends; The kinetic energy that gas obtains stepped centrifugal compressor impeller 21 places in Diffuser is converted into pressure energy to continue improving pressure, and this part air-flow is a low-pressure air current; Another part air communication is crossed the back vaneless diffuser 29 that major diameter impeller outlet rear end 27 gets near gas compressor back cover 23; Because the time that this part air-flow stops in stepped centrifugal compressor impeller 21 is longer; Stepped centrifugal compressor impeller 21 is more to its acting; It is bigger to receive centrifugal force, makes this strand air-flow have higher pressure energy and kinetic energy entering Diffuser diffusion.Two strands of different air-flows of pressure ratio are carried out gas and are collected by gas collection runner spiral case 16, back gas collection runner spiral case 24 before the gas compressor respectively after passing through double flow channel vaneless diffuser 25.
Embodiment 2: like Fig. 5, shown in Figure 6, present embodiment and embodiment's 1 difference are the impeller shape difference to some extent among stepped centrifugal compressor impeller 21 and the embodiment 1.Present embodiment is opposite with embodiment 1, and impeller outlet is designed to major diameter near gas compressor fore shell 15 ends, is designed to minor diameter near gas compressor back cover 23 ends.Remaining part and embodiment 1 are identical.
Identical in the present embodiment among flow basic and the embodiment 1 of air-flow; Air-flow flows to impeller outlet 28 behind compressor inlet 20 and impeller 21; Air-flow is divided into two strands; One is through the preceding vaneless diffuser 22 that major diameter impeller outlet front end 35 gets near gas compressor fore shell 15 ends, and this strand air-flow is a high pressure draught; The back vaneless diffuser 29 that another strand gets near gas compressor back cover 23 ends through minor diameter impeller outlet rear end 36, this strand air-flow is a low-pressure air current.Two strands of different air-flows of pressure ratio are carried out gas and are collected by gas collection runner spiral case 16, back gas collection runner spiral case 24 before the gas compressor respectively after passing through double flow channel vaneless diffuser 25.
In sum, more than being merely preferred embodiment of the present invention, is not to be used to limit protection scope of the present invention.All within spirit of the present invention and principle, any modification of being done, be equal to replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (6)
1. a centrifugal compressor that is used to produce two kinds of different pressure ratios is characterized in that, comprising: gas compressor fore shell, gas compressor back cover, annular slab and stepped centrifugal compressor impeller; Wherein, the gas compressor fore shell is provided with compressor air inlet machine mouth and the preceding gas collection runner spiral case of gas compressor; The gas compressor back cover is provided with gas collection runner spiral case behind the gas compressor; Before the gas compressor behind gas collection runner spiral case and the gas compressor gas collection runner spiral case be fixedly connected; And clamping annular slab between its connection part; Part outside the annular slab clamp face is annular flow distribution plate; At gas compressor fore shell and gas compressor back cover inside stepped centrifugal compressor impeller is installed, it is stepped that stepped centrifugal compressor impeller makes its outlet port form two-stage, and a side plane of annular flow distribution plate is corresponding to the step surface position of stepped centrifugal compressor impeller outlet two-stage step; The annular flow distribution plate is divided into two the diffusion passage of gas compressor fore shell diffusion wall and gas compressor back cover diffusion wall composition; Near gas compressor fore shell end be preceding vaneless diffuser, near gas compressor back cover end be the back vaneless diffuser, preceding vaneless diffuser with the back vaneless diffuser form the double flow channel vaneless diffuser jointly.
2. the centrifugal compressor that is used to produce two kinds of different pressure ratios as claimed in claim 1 is characterized in that, said stepped centrifugal compressor impeller outlet is designed to minor diameter near gas compressor fore shell end, is designed to major diameter near gas compressor back cover end.
3. the centrifugal compressor that is used to produce two kinds of different pressure ratios as claimed in claim 1 is characterized in that, said stepped centrifugal compressor impeller outlet is designed to major diameter near gas compressor fore shell end, is designed to minor diameter near gas compressor back cover end.
4. like claim 1, the 2 or 3 described centrifugal compressors that are used to produce two kinds of different pressure ratios; It is characterized in that; Gas collection runner spiral case exterior boss is provided with the fore shell bolt hole before the gas compressor of said gas compressor fore shell; Gas collection runner spiral case exterior boss is provided with the back cover bolt hole behind the gas compressor of said gas compressor back cover, and the back cover bolt hole is corresponding with fore shell bolt hole on the gas compressor fore shell boss, and inserting bolt is connected the gas compressor fore shell and tightens together with the gas compressor back cover.
5. the centrifugal compressor that is used to produce two kinds of different pressure ratios as claimed in claim 4 is characterized in that, is processed with annular boss and the annular groove that cooperatively interacts on the junction surface of said gas compressor fore shell and gas compressor back cover respectively.
6. the centrifugal compressor that is used to produce two kinds of different pressure ratios as claimed in claim 5 is characterized in that, said annular flow distribution plate surface Machining has along the radially stiffening rib that circumferentially is uniformly distributed with.
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| CN201210365320.8A CN102840169B (en) | 2012-09-26 | 2012-09-26 | Centrifugal compressor used for generating two different pressure ratios |
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| CN201210365320.8A CN102840169B (en) | 2012-09-26 | 2012-09-26 | Centrifugal compressor used for generating two different pressure ratios |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103438026A (en) * | 2013-09-09 | 2013-12-11 | 中国航空动力机械研究所 | Centrifugal air compressor with intermediate-stage air entrainment function |
| CN104500452A (en) * | 2014-12-16 | 2015-04-08 | 中国科学院工程热物理研究所 | Vaneless diffusion section structure with regular N-prism side outlet and machining method |
| CN105065109A (en) * | 2015-08-06 | 2015-11-18 | 中国北方发动机研究所(天津) | Wide-flow-range turbocharger |
| CN105065330A (en) * | 2015-08-06 | 2015-11-18 | 中国北方发动机研究所(天津) | Gas compressor structure of double-gas-inflow turbocharger under share diffuser |
| CN106382258A (en) * | 2016-12-06 | 2017-02-08 | 深圳福世达动力科技有限公司 | Centrifugal contra-rotating ram compressor |
| CN106837860A (en) * | 2017-02-23 | 2017-06-13 | 深圳福世达动力科技有限公司 | Double pressure ratio centrifugal compressors |
| CN106895012A (en) * | 2017-05-05 | 2017-06-27 | 大连依勒斯涡轮增压技术有限公司 | A kind of compact two-step supercharging compressor |
| CN114876831A (en) * | 2022-04-26 | 2022-08-09 | 杭州老板电器股份有限公司 | Volute structure and range hood |
| CN116591971A (en) * | 2023-07-17 | 2023-08-15 | 西北工业大学 | Double-channel centrifugal compressor with high-low pressure ratio |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3208213A (en) * | 1963-05-20 | 1965-09-28 | British Ship Res Ass | Supercharger for an internal combustion engine |
| US3829235A (en) * | 1971-11-26 | 1974-08-13 | Wallace Murray Corp | Turbocharger compressor with dual collector chambers |
| US5025629A (en) * | 1989-03-20 | 1991-06-25 | Woollenweber William E | High pressure ratio turbocharger |
| CN2257861Y (en) * | 1994-09-24 | 1997-07-16 | 孙敏超 | Mixed-flow turbocharger |
| US6062028A (en) * | 1998-07-02 | 2000-05-16 | Allied Signal Inc. | Low speed high pressure ratio turbocharger |
| US6651431B1 (en) * | 2002-08-28 | 2003-11-25 | Ford Global Technologies, Llc | Boosted internal combustion engines and air compressors used therein |
-
2012
- 2012-09-26 CN CN201210365320.8A patent/CN102840169B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3208213A (en) * | 1963-05-20 | 1965-09-28 | British Ship Res Ass | Supercharger for an internal combustion engine |
| US3829235A (en) * | 1971-11-26 | 1974-08-13 | Wallace Murray Corp | Turbocharger compressor with dual collector chambers |
| US5025629A (en) * | 1989-03-20 | 1991-06-25 | Woollenweber William E | High pressure ratio turbocharger |
| CN2257861Y (en) * | 1994-09-24 | 1997-07-16 | 孙敏超 | Mixed-flow turbocharger |
| US6062028A (en) * | 1998-07-02 | 2000-05-16 | Allied Signal Inc. | Low speed high pressure ratio turbocharger |
| US6651431B1 (en) * | 2002-08-28 | 2003-11-25 | Ford Global Technologies, Llc | Boosted internal combustion engines and air compressors used therein |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103438026A (en) * | 2013-09-09 | 2013-12-11 | 中国航空动力机械研究所 | Centrifugal air compressor with intermediate-stage air entrainment function |
| CN104500452A (en) * | 2014-12-16 | 2015-04-08 | 中国科学院工程热物理研究所 | Vaneless diffusion section structure with regular N-prism side outlet and machining method |
| CN105065109A (en) * | 2015-08-06 | 2015-11-18 | 中国北方发动机研究所(天津) | Wide-flow-range turbocharger |
| CN105065330A (en) * | 2015-08-06 | 2015-11-18 | 中国北方发动机研究所(天津) | Gas compressor structure of double-gas-inflow turbocharger under share diffuser |
| CN106382258A (en) * | 2016-12-06 | 2017-02-08 | 深圳福世达动力科技有限公司 | Centrifugal contra-rotating ram compressor |
| CN106837860A (en) * | 2017-02-23 | 2017-06-13 | 深圳福世达动力科技有限公司 | Double pressure ratio centrifugal compressors |
| CN106895012A (en) * | 2017-05-05 | 2017-06-27 | 大连依勒斯涡轮增压技术有限公司 | A kind of compact two-step supercharging compressor |
| CN114876831A (en) * | 2022-04-26 | 2022-08-09 | 杭州老板电器股份有限公司 | Volute structure and range hood |
| CN116591971A (en) * | 2023-07-17 | 2023-08-15 | 西北工业大学 | Double-channel centrifugal compressor with high-low pressure ratio |
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| Publication number | Publication date |
|---|---|
| CN102840169B (en) | 2015-03-18 |
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