CN102840169B - 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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- CN102840169B CN102840169B CN201210365320.8A CN201210365320A CN102840169B CN 102840169 B CN102840169 B CN 102840169B CN 201210365320 A CN201210365320 A CN 201210365320A CN 102840169 B CN102840169 B CN 102840169B
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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 a kind of compressor apparatus of internal-combustion engine turbosupercharger, and particularly a kind of centrifugal compressor device for generation of two kinds of different pressure ratios, belongs to supercharging of internal combustion engine technical field.
Background technique
At present, the pressurized machine that most of vehicle internal combustion engine mates is ordinary single-stage turbosupercharger.When automobile travels on Plain, the pressure ratio that single-stage supercharger produces generally can reach the coupling requirement of internal-combustion engine.But, when automobile enters plateau, by the restriction of pressurized machine pressure ratio, rotating speed and range of flow, there will be air-intake of combustion engine quantity not sufficient, power drop, supercharger speed raises, operation point enters the phenomenons such as nonclient area, single-stage supercharger often can not adapt to the severe working environment in plateau.This just needs to introduce a kind of high-pressure system, working state when Two Stage Turbocharging System can make internal-combustion engine return to Plain under altitude environment as a kind of high-pressure system with the obvious advantage.But this pressurization system structurally needs layout two pressurized machines, not only increase the difficulty of confined space inner piece compact Layout, and plains region is travelled on for the most of the time or only needs single-stage supercharger just can meet the situation of supercharging of internal combustion engine requirement, add the complexity that internal combustion engine runs undoubtedly.
Miniature gas turbine more and more received the concern of people in recent years as a kind of auxiliary power unit, miniature gas turbine is applied to Two Stage Turbocharging System, and gas turbine drives additional mechanical supercharging gas compressor can be made as the low pressure stage gas compressor of Two Stage Turbocharging System.The patent that publication number is " Cn102155290 " relates to a kind of auxiliary pressurization system, as shown in Figure 1, internal combustion engine is when low altitude area, switching valve 9 only makes air be communicated with air filter 10, rely on main pressurization system (in Fig. 1 dashed region) normally mate with internal-combustion engine 13 and work, its working principle and common boosting internal combustion engine are as good as.When internal combustion engine is in high altitude localities, adopt high-pressure air supply firing chamber 6 across-the-line starting auxiliary pressurization system, first fresh air by after auxiliary air filter 1, enters 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 firing chamber 6 by solenoid valve fueling injection equipment 5, fuel oil through atomization mixes with the pressurized air from auxiliary combustion gas compressor 3, by combustion chamber ignition device 7, gas mixture is lighted, the high-temperature fuel gas produced promotes auxiliary turbine 4 expansion work, to drive additional mechanical supercharging gas compressor 2 and auxiliary combustion gas compressor 3, control system 8 regulates the working condition of auxiliary pressurization system according to boost pressure.After the pressurized air flowed out by additional mechanical supercharging gas compressor 2 flows through switching valve 9 and air filter 10, enter into gas compressor 11 and be further compressed, temperature and pressure continues to improve, and then cools through intercooler 12, reduces temperature and the volume flowrate of air.After such pressurization, air enters internal-combustion engine 13 and fuel oil mixed combustion, and the high-temp waste gas that burning produces enters into turbine 14 expansion work of main pressurization system, and to drive its gas compressor 11, the waste gas after turbine 14 expands enters air.
Not only to drive auxiliary combustion gas compressor 3 because auxiliary turbine 4 does work, also will drive additional mechanical supercharging gas compressor 2, define the structural type of a turbine and two gas compressor series connection.This form makes whole rotor-support-foundation system long, thus add rotor disequilibrium, the flex resistance of rotor-support-foundation system and rigidity proposed to high requirement, increase wearing and tearing and reduce mechanical efficiency, so need to improve this kind of structural type, two gas compressors are united two into one.But the pressure ratio needed for auxiliary combustion gas compressor is generally more than 3.0, and as gas compressor rudimentary in two-stage supercharger additional mechanical supercharging gas compressor needed for pressure ratio be generally 1.3 ~ 2.0.Therefore, need to design a kind of centrifugal compressor taking into account auxiliary combustion gas compressor and additional mechanical supercharging gas compressor function.
Summary of the invention
In view of this, the invention provides a kind of centrifugal compressor for generation of two kinds of different pressure ratios, both meet the pressure ratio requirement of auxiliary combustion gas compressor, also meet the pressure ratio requirement of additional mechanical supercharging gas compressor simultaneously.
To achieve these goals, the technical solution adopted in the present invention is:
For generation of a centrifugal compressor for two kinds of different pressure ratios, comprise gas compressor fore shell, gas compressor back cover, annular slab and stepped centrifugal compressor impeller, wherein, wherein, gas compressor fore shell is provided with gas collection channel volute before compressor air inlet machine mouth and gas compressor, gas compressor back cover is provided with gas collection channel volute after gas compressor, before gas compressor, gas collection channel volute is fixedly connected with gas collection channel volute after gas compressor, and clamping annular slab between its connection part, part outside 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, sized by the impeller outlet of described stepped centrifugal compressor impeller, that impeller outlet place is formed is stepped for two kinds of diameters, one side plane of annular flow distribution plate corresponds to the step surface position of stepped centrifugal compressor impeller outlet two-stage step, annular flow distribution plate and step surface leave gap, this gap does not affect the rotation of stepped centrifugal compressor impeller, the diffusion passage of gas compressor fore shell diffusion wall and gas compressor back cover diffusion wall composition is divided into two by annular flow distribution plate, near gas compressor fore shell end is front vaneless diffuser, near gas compressor back cover end is rear vaneless diffuser, front vaneless diffuser and rear vaneless diffuser form double flow channel vaneless diffuser jointly.
Before the gas compressor of described gas compressor fore shell, gas collection channel volute exterior boss is provided with fore shell bolt hole.
After the gas compressor of described gas compressor back cover, gas collection channel volute exterior boss is provided with rear shell bolt hole, and rear shell bolt hole is corresponding with the fore shell bolt hole on gas compressor fore shell boss, and gas compressor fore shell is connected with gas compressor back cover and tightens together by inserting bolt.
The junction surface of described gas compressor fore shell and gas compressor back cover is processed with respectively the annular boss and annular groove that cooperatively interact, is beneficial to the installation location of gas compressor fore shell and gas compressor back cover.
Described annular slab surface Machining has circumferentially uniform radial reinforced rib, for increasing its intensity and rigidity;
As a kind of technological scheme, described stepped centrifugal compressor impeller outlet is designed to minor diameter near gas compressor fore shell end, major diameter is designed near gas compressor back cover end, as another kind of technological scheme, described 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 described double flow channel vaneless diffuser collect the different gas of two strands of pressure being 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, take into account the function of auxiliary combustion gas compressor and additional mechanical supercharging gas compressor, in system two gas compressors are united two into one, overall structure is simplified, and improves balancing rotor simultaneously, reduces requirement to rotor-support-foundation system flex resistance and rigidity, reduces system mechanics and wear and tear and improve mechanical efficiency.
2, the present invention also can be applicable under other need generation two kinds of compressed-air actuated situations of pressure ratio.
Accompanying drawing explanation
Fig. 1 be in background technique of the present invention for recovering the high motive combustion engine type auxiliary pressurization system schematic diagram of internal-combustion engine.
Fig. 2 is the structural representation of the centrifugal compressor device for generation of two kinds of different pressure ratios in the embodiment of the present invention 1.
Fig. 3 is the structural representation of the annular slab in the present invention.
Fig. 4 is the stepped centrifugal compressor impeller structural representation in the embodiment of the present invention 1.
Fig. 5 is the structural representation of the centrifugal compressor device for generation of two kinds of different pressure ratios in the embodiment of the present invention 2.
Fig. 6 is the stepped centrifugal compressor impeller structural representation in the embodiment of the present invention 2.
In figure: 1-assists air filter, 2-additional mechanical supercharging gas compressor, 3-auxiliary combustion gas compressor, 4-auxiliary turbine, 5-solenoid valve fueling injection equipment, 6-firing chamber, 7-ignition mechanism, 8-starts and control system, 9-switching valve, 10-air filter, 11-gas compressor, 12-intercooler, 13-internal-combustion engine, 14-turbine, 15-gas compressor fore shell, gas collection channel volute before 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 22-, 23-gas compressor back cover, gas collection channel volute after 24-gas compressor, 25-double flow channel vaneless diffuser, 26-gas compressor back cover diffusion wall, 27-major diameter impeller outlet rear end, 28-impeller outlet, vaneless diffuser after 29-, 30-fore shell bolt hole, 31-rear shell bolt hole, 33-stiffening rib, 34-annular flow distribution plate, 35-major diameter impeller outlet front end, 36-minor diameter impeller outlet rear end.
Embodiment
To develop simultaneously embodiment below in conjunction with accompanying drawing, describe the present invention.
Embodiment 1: as shown in Figure 2, a kind of centrifugal compressor device for generation of 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 gas collection channel volute 16 before compressor air inlet machine mouth 20 and gas compressor; Gas compressor back cover 23 is provided with gas collection channel volute 24 after gas compressor, gas compressor fore shell 15 and gas compressor back cover 23 with bolts, and clamping has annular slab 17 therebetween, and the part beyond annular slab 17 clamp face is annular flow distribution plate 34; The diffusion passage that gas compressor fore shell diffusion wall 18 and gas compressor back cover diffusion wall 26 form is divided into two by annular flow distribution plate 34, defines double flow channel vaneless diffuser 25; Be provided with stepped centrifugal compressor impeller 21 in gas compressor fore shell 15 and gas compressor back cover 23 inside, sized by impeller outlet 28, that impeller outlet place is formed is stepped for two kinds of diameters.
Described gas compressor fore shell 15 is provided with gas collection channel volute 16 before compressor air inlet machine mouth 20 and gas compressor, and scroll outer boss is provided with fore shell bolt hole 30.
Described gas compressor back cover 23 is provided with gas collection channel volute 24 after gas compressor, scroll outer boss is provided with rear shell bolt hole 31, rear shell bolt hole 31 is corresponding with the fore shell bolt hole 30 on gas compressor fore shell boss, and gas compressor fore shell 15 is connected with gas compressor back cover 23 and tightens together by inserting bolt.
The junction surface of described gas compressor fore shell 15 and gas compressor back cover 23 is processed with respectively the annular boss and annular groove that cooperatively interact,
As shown in Figure 3, described annular slab 17 surface Machining has circumferentially uniform radial reinforced rib 33, for increasing its intensity and rigidity.Annular slab 17 to be clamped in before gas compressor after gas collection channel volute 16 and gas compressor between gas collection channel volute 24, the diffusion passage that gas compressor fore shell diffusion wall 18 and gas compressor back cover diffusion wall 26 form is divided into two by annular flow distribution plate 34, near gas compressor fore shell 15 end is front vaneless diffuser 22, near gas compressor back cover 22 end is rear vaneless diffuser 29, and front vaneless diffuser 22 and rear vaneless diffuser 29 define double flow channel vaneless diffuser 25.
Two runners of described double flow channel vaneless diffuser 25 collect the different gas of two strands of pressure being produced by stepped centrifugal compressor impeller 21 respectively.
As shown in Figure 4, described stepped centrifugal compressor impeller 21, its impeller outlet 28 forms 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 enters gas compressor by compressor inlet 20, gas compressor stepped centrifugal compressor impeller 21 part is flowed into along inlet channel, stepped centrifugal compressor impeller 21 and rotor thereof carry out rotation motion owing to driving by turbine or other power equipments, and air-flow and then makes High Rotation Speed under the drive of stepped centrifugal compressor impeller 21 blade.Gas is due to the effect by rotary centrifugal force, and the diffusion flowing in stepped centrifugal compressor impeller 21, and gas pressure in stepped centrifugal compressor impeller 21 is improved gradually.Part air-flow enters vaneless diffuser 22 before gas compressor fore shell 15 end by minor diameter impeller outlet front end 19, in Diffuser, the kinetic transformation that stepped centrifugal compressor impeller 21 place obtains is pressure energy to continue to improve pressure by gas, and this part air-flow is low-pressure air current; Another part air-flow enters the rear vaneless diffuser 29 near gas compressor back cover 23 by major diameter impeller outlet rear end 27, the time stopped in stepped centrifugal compressor impeller 21 due to this part air-flow is longer, stepped centrifugal compressor impeller 21 is more to its acting, be subject to centrifugal force larger, make this strand of air-flow have higher pressure energy and kinetic energy enters Diffuser diffusion.The different air-flow of two bursts of pressure ratios after double flow channel vaneless diffuser 25 respectively by gas compressor before gas collection channel volute 16, after gas collection channel volute 24 carry out gas collection.
Embodiment 2: as shown in Figure 5, Figure 6, and the present embodiment difference from Example 1 is stepped centrifugal compressor impeller 21 and the impeller shape difference to some extent in embodiment 1.The present embodiment is contrary with embodiment 1, and impeller outlet is designed to major diameter near gas compressor fore shell 15 end, is designed to minor diameter near gas compressor back cover 23 end.Remaining part is identical with embodiment 1.
Identical substantially with embodiment 1 of the flowing of air-flow in the present embodiment, air-flow flows to impeller outlet 28 after compressor inlet 20 and impeller 21, air-flow is divided into two strands, one enters vaneless diffuser 22 before gas compressor fore shell 15 end by major diameter impeller outlet front end 35, and this strand of air-flow is high pressure draught; Another strand enters the rear vaneless diffuser 29 near gas compressor back cover 23 end by minor diameter impeller outlet rear end 36, and this strand of air-flow is low-pressure air current.The different air-flow of two bursts of pressure ratios after double flow channel vaneless diffuser 25 respectively by gas compressor before gas collection channel volute 16, after gas collection channel volute 24 carry out gas collection.
In sum, these are only preferred embodiment of the present invention, be not intended to limit protection scope of the present invention.Within the spirit and principles in the present invention all, any amendment done, equivalent replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (2)
1. for generation of a centrifugal compressor for two kinds of different pressure ratios, it is characterized in that, comprising: gas compressor fore shell, gas compressor back cover, annular slab and stepped centrifugal compressor impeller, wherein, gas compressor fore shell is provided with gas collection channel volute before compressor air inlet machine mouth and gas compressor, gas compressor back cover is provided with gas collection channel volute after gas compressor, before gas compressor, gas collection channel volute is fixedly connected with gas collection channel volute after gas compressor, and clamping annular slab between its connection part, part outside 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, sized by the impeller outlet of described stepped centrifugal compressor impeller, that impeller outlet place is formed is stepped for two kinds of diameters, one side plane of annular flow distribution plate corresponds to the step surface position of stepped centrifugal compressor impeller outlet two-stage step, the diffusion passage of gas compressor fore shell diffusion wall and gas compressor back cover diffusion wall composition is divided into two by annular flow distribution plate, near gas compressor fore shell end is front vaneless diffuser, near gas compressor back cover end is rear vaneless diffuser, front vaneless diffuser and rear vaneless diffuser form double flow channel vaneless diffuser jointly.
2. as claimed in claim 1 for generation of the centrifugal compressor of two kinds of different pressure ratios, it is characterized in that, described 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. as claimed in claim 1 for generation of the centrifugal compressor of two kinds of different pressure ratios, it is characterized in that, described 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. the centrifugal compressor for generation of two kinds of different pressure ratios as described in claim 1,2 or 3, it is characterized in that, before the gas compressor of described gas compressor fore shell, gas collection channel volute exterior boss is provided with fore shell bolt hole, after the gas compressor of described gas compressor back cover, gas collection channel volute exterior boss is provided with rear shell bolt hole, rear shell bolt hole is corresponding with the fore shell bolt hole on gas compressor fore shell boss, and gas compressor fore shell is connected with gas compressor back cover and tightens together by inserting bolt.
5., as claimed in claim 4 for generation of the centrifugal compressor of two kinds of different pressure ratios, it is characterized in that, the junction surface of described gas compressor fore shell and gas compressor back cover is processed with respectively the annular boss and annular groove that cooperatively interact.
6., as claimed in claim 5 for generation of the centrifugal compressor of two kinds of different pressure ratios, it is characterized in that, described annular flow distribution plate surface Machining has circumferentially uniform radial reinforced rib.
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| Application Number | Priority Date | Filing Date | Title |
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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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| Application Number | Priority Date | Filing Date | Title |
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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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| CN102840169A CN102840169A (en) | 2012-12-26 |
| CN102840169B true CN102840169B (en) | 2015-03-18 |
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Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103438026B (en) * | 2013-09-09 | 2018-05-01 | 中国航空动力机械研究所 | The centrifugal compressor of intergrade bleed |
| CN104500452B (en) * | 2014-12-16 | 2016-08-31 | 中国科学院工程热物理研究所 | A kind of vaneless diffuser structure and machining method with positive N prism side exit |
| 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 |
| CN105065109A (en) * | 2015-08-06 | 2015-11-18 | 中国北方发动机研究所(天津) | Wide-flow-range turbocharger |
| 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 |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1082792A (en) * | 1963-05-20 | 1967-09-13 | British Ship Res Ass | A supercharger for an internal combustion engine |
| BE791867A (en) * | 1971-11-26 | 1973-05-24 | Wallace Murray Corp | DUAL COLLECTOR TURBOCHARGER COMPRESSOR |
| 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 |
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