CN103244258B - A kind of turbo charge system being applicable to single cylinder diesel - Google Patents
A kind of turbo charge system being applicable to single cylinder diesel Download PDFInfo
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- CN103244258B CN103244258B CN201310173924.7A CN201310173924A CN103244258B CN 103244258 B CN103244258 B CN 103244258B CN 201310173924 A CN201310173924 A CN 201310173924A CN 103244258 B CN103244258 B CN 103244258B
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- waste gas
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- cylinder diesel
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- 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
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Abstract
The invention discloses a kind of turbo charge system being applicable to single cylinder diesel, comprise the turbosupercharger primarily of gas compressor and turbine composition, be arranged in parallel the first identical exhausting waste gas pipeline of caliber and the second exhausting waste gas pipeline between the exhaust valve of the cylinder of single cylinder diesel and the suction port of turbine, the length of the second exhausting waste gas pipeline is greater than the length of the first exhausting waste gas pipeline, advantage is that the waste gas dredged by the first exhausting waste gas pipeline and the second exhausting waste gas pipeline enters into turbine in the different moment, namely the waste gas dredged by the first exhausting waste gas pipeline and the second exhausting waste gas pipeline is entered into turbine and there is a time difference, and this time difference is determined by the length of the first exhausting waste gas pipeline and the second exhausting waste gas pipeline, turbine control mode is entered by this waste gas, to efficiently solve in single cylinder diesel work the long and problem flowing to the waste gas instability in turbine that causes of exhaust interval, thus facilitate single cylinder diesel enforcement turbosupercharging.
Description
Technical field
The present invention relates to a kind of turbo charge system, especially relate to a kind of turbo charge system being applicable to single cylinder diesel.
Background technique
Turbo charge system is widely used on multicylinder engine.And when existing turbo charge system is applied on single cylinder diesel, because in single cylinder diesel work, exhaust interval is longer, therefore the waste gas flowing into turbine is very unstable, so just make when pressure wave enters into turbine, turbine accelerates, and when pressure weakens, because of gas compressor absorbed power, turbine is tending towards slowing down, cause utilizing of exhaust energy very poor, thus cause single cylinder diesel to be difficult to carry out turbosupercharging.
Summary of the invention
Technical problem to be solved by this invention is to provide a kind of turbo charge system being applicable to single cylinder diesel, and its structure is simple, and the problem flowing to the waste gas instability in turbine that effectively can solve exhaust interval length in single cylinder diesel work and cause.
The present invention solves the problems of the technologies described above adopted technological scheme: a kind of turbo charge system being applicable to single cylinder diesel, comprise the turbosupercharger primarily of gas compressor and turbine composition, it is characterized in that: be arranged in parallel the first identical exhausting waste gas pipeline of caliber and the second exhausting waste gas pipeline between the exhaust valve of the cylinder of described single cylinder diesel and the suction port of described turbine, the length of the second described exhausting waste gas pipeline is greater than the length of the first described exhausting waste gas pipeline, at this, the the first exhausting waste gas pipeline utilizing caliber identical and the second exhausting waste gas pipeline are dredged the waste gas that single cylinder diesel is discharged, length due to the second exhausting waste gas pipeline is greater than the length of the first exhausting waste gas pipeline, therefore the waste gas dredged by the first exhausting waste gas pipeline and the second exhausting waste gas pipeline enters into turbine in the different moment, namely the waste gas dredged by the first exhausting waste gas pipeline and the second exhausting waste gas pipeline is entered into turbine and there is a time difference, and this time difference is determined by the length of the first exhausting waste gas pipeline and the second exhausting waste gas pipeline, this mode entering the time lag of turbine by controlling waste gas, to efficiently solve in single cylinder diesel work the long and problem flowing to the waste gas instability in turbine that causes of exhaust interval, thus facilitate single cylinder diesel enforcement turbosupercharging.
The length difference Δ L of the second described exhausting waste gas pipeline and the first described exhausting waste gas pipeline is: Δ L=V
ex× 60/4n, wherein, V
exthe speed of the air-flow in the second exhausting waste gas pipeline described in expression and the first described exhausting waste gas pipeline, n represents the rotating speed of single cylinder diesel.
The suction port of described gas compressor is connected with air intake conduit, the air outlet of described gas compressor is connected with pressurization gas discharge conduit, between the intake valve of the air outlet of described pressurization gas discharge conduit and the cylinder of described single cylinder diesel, is provided with gas holder, at this, because the intake valve of the crank angle range inner casing at nearly 500 ° is closed, volume time non pressurized being the pipeline (pressurization gas discharge conduit) of cylinder supply pressurization gas is less, when the exhaust valve of cylinder is opened, the pressure of pressurization gas unloads instantaneously, so just be difficult to countercylinder inflation effectively, therefore the gas holder of a large volume is set between the air outlet of pressurization gas discharge conduit and the intake valve of the cylinder of single cylinder diesel, this gas holder is for storing a certain amount of pressurized gas, can countercylinder inflation fully when the intake valve of cylinder is opened.
The air outlet of described gas compressor is connected by the suction port of pressurization gas flow pipe with described turbine, described pressurization gas flow pipe is provided with the first one-way valve, the air outlet of described gas compressor is connected by the suction port of pressurization gas return line with described gas compressor, and described pressurization gas return line is provided with the second one-way valve, at this, for four-stroke horizontal bar diesel engine, single cylinder diesel is in a work cycle, except the air inlet processes of about 220 °, the intake valve of the crank angle time inner casing of about 500 ° is closed, the exhaust valve of cylinder is like this too, and turbosupercharger is also in rotation status due to inertia, in order to avoid the compressor surge (obstruction) caused thus, therefore a pressurization gas flow pipe is set between the air outlet and the suction port of turbine of gas compressor, a pressurization gas return line is set between the air outlet of gas compressor and the suction port of gas compressor, and first one-way valve is set on pressurization gas flow pipe, pressurization gas return line arranges second one-way valve, when the boost pressure of the pressurization gas of discharging when the air outlet of gas compressor is like this lower than required boost pressure, pressurization gas directly enters in the cylinder of single cylinder diesel by pressurization gas discharge conduit, when the boost pressure of the pressurization gas of discharging when the air outlet of gas compressor is greater than or equal to required boost pressure, open the first one-way valve, pressurization gas flows into turbine through pressurization gas flow pipe, turbine expansion (impacts) acting, open the second one-way valve when intake valve and first closed check valve of cylinder, now pressurization gas is back to the suction port place of gas compressor by pressurization gas return line, efficiently avoid compressor surge.
The first described one-way valve and the second described one-way valve are pressure opening and closing valve.
The air outlet of described turbine is connected with exhaust emission tube road.
The structure of the second described exhausting waste gas pipeline is flute profile, the second described exhausting waste gas pipeline comprises two lateral canals and a connecting tube, one end of side pipe described in first is communicated with one end of the first described exhausting waste gas pipeline, the other end of the side pipe described in first is communicated with one end of described connecting tube, one end of side pipe described in second is communicated with the other end of the first described exhausting waste gas pipeline, and the other end of the side pipe described in second is communicated with the other end of described connecting tube.
Compared with prior art, the invention has the advantages that: by being arranged in parallel the first identical exhausting waste gas pipeline of caliber and the second exhausting waste gas pipeline between the exhaust valve of the cylinder at single cylinder diesel and the suction port of turbine, and require that the length of the second exhausting waste gas pipeline is greater than the length of the first exhausting waste gas pipeline, the waste gas dredged by the first exhausting waste gas pipeline and the second exhausting waste gas pipeline like this enters into turbine in the different moment, namely the waste gas dredged by the first exhausting waste gas pipeline and the second exhausting waste gas pipeline is entered into turbine and there is a time difference, and this time difference is determined by the length of the first exhausting waste gas pipeline and the second exhausting waste gas pipeline, this mode entering the time lag of turbine by controlling waste gas, to efficiently solve in single cylinder diesel work the long and problem flowing to the waste gas instability in turbine that causes of exhaust interval, thus facilitate single cylinder diesel enforcement turbosupercharging, achieve the power-lift to single cylinder diesel and discharge improvement.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of turbo charge system of the present invention.
Embodiment
Below in conjunction with accompanying drawing, embodiment is described in further detail the present invention.
A kind of turbo charge system being applicable to single cylinder diesel that the present invention proposes, its schematic diagram as shown in Figure 1, it comprises the turbosupercharger formed primarily of gas compressor C and turbine T, the suction port of gas compressor C is connected with air intake conduit 1, the suction port of air intake conduit 1 passes into air, the air outlet of gas compressor C is connected with pressurization gas discharge conduit 2, gas holder 3 is provided with between the intake valve of the air outlet of pressurization gas discharge conduit 2 and the cylinder cyl of single cylinder diesel, the air outlet of gas compressor C is connected by the suction port of pressurization gas flow pipe 4 with turbine T, pressurization gas flow pipe 4 is provided with the first one-way valve 5, the air outlet of gas compressor C is connected by the suction port of pressurization gas return line 6 with gas compressor C, pressurization gas return line 6 is provided with the second one-way valve 7, the first exhausting waste gas pipeline 81 and the second exhausting waste gas pipeline 82 that caliber is identical is arranged in parallel between the exhaust valve of the cylinder cyl of single cylinder diesel and the suction port of turbine T, the length of the second exhausting waste gas pipeline 82 is greater than the length of the first exhausting waste gas pipeline 81, the air outlet of turbine T is connected with exhaust emission tube road 9, the air outlet combustion gas on exhaust emission tube road 9 is in air.
During turbo charge system work of the present invention, when the exhaust valve of the cylinder cyl of single cylinder diesel is opened, speed, the flow of supposing the air-flow in the second exhausting waste gas pipeline 82 and the first exhausting waste gas pipeline 81 are equal, then can obtain air-flow enters into turbine T time difference Δ t through the second exhausting waste gas pipeline 82 and the first exhausting waste gas pipeline 81, Δ t=V
ex/ L
2-V
ex/ L
1, v represents the speed of air-flow, L
2represent the length of the second exhausting waste gas pipeline 82, L
1represent the length of the first exhausting waste gas pipeline 81, from Δ t=V
ex/ L
2-V
ex/ L
1in can find out, by the length of the length and the first exhausting waste gas pipeline 81 that design the second exhausting waste gas pipeline 82, the time lag that waste gas enters into turbine T can be controlled, this addresses the problem the long and problem entering into the air-flow instability of turbine that causes of single cylinder diesel exhaust interval, facilitate the turbosupercharging of single cylinder diesel.At this, the length difference of the length of the second exhausting waste gas pipeline 82 and the length of the first exhausting waste gas pipeline 81 can calculate according to the phase angle of the speed of the air-flow in pipeline and single cylinder diesel, if the speed supposing air-flow is V
ex, the rotating speed of single cylinder diesel is n, then both length difference Δ L can be set to Δ L=V when designing the second exhausting waste gas pipeline 82 and the first exhausting waste gas pipeline 81
ex× 60/4n, the discharge capacity of single cylinder diesel and the linear loss of pipeline is considered in actual mechanical process, the length difference of the second exhausting waste gas pipeline 82 and the first exhausting waste gas pipeline 81 can be controlled within 1 meter, if make accurate Calculation to pipeline section shape and area, then can be controlled in 0.5 meter.
When specific design second exhausting waste gas pipeline 82, for anufacturability, second exhausting waste gas pipeline 82 can be designed to flute profile, namely three sections of pipelines are comprised, two lateral canals and a connecting tube, one end of first lateral canal is communicated with one end of the first exhausting waste gas pipeline 81, the other end of the first lateral canal is communicated with one end of connecting tube, one end of second lateral canal is communicated with the other end of the first exhausting waste gas pipeline 81, the other end of the second lateral canal is communicated with the other end of connecting tube, at this, connecting tube is one section of straight pipeline.
In this particular embodiment, the first one-way valve 5 and the second one-way valve 7 all adopt existing pressure opening and closing valve, as adopted the pressure opening and closing valve of existing spring during specific operation.
Main process during turbo charge system work of the present invention is: during work, air enters in gas compressor by air intake conduit, the pressurization gas that air is formed after gas compressor compression enters in gas holder by pressurization gas discharge conduit, and the cylinder of the pressurization gas in gas holder to single cylinder diesel is inflated; During single cylinder diesel waste air, the exhaust valve of the cylinder of single cylinder diesel is opened, the waste gas part that single cylinder diesel is discharged enters in turbine by the first exhausting waste gas pipeline, another part enters in turbine by the second exhausting waste gas pipeline, length due to the second exhausting waste gas pipeline is greater than the length of the first exhausting waste gas pipeline, is therefore entered the waste gas life period interval of turbine by the first exhausting waste gas pipeline and the second exhausting waste gas pipeline.When the too high generation of gas compressor end air pressure is blocked, air-flow is back to the suction port of gas compressor through the second one-way valve, also can flow into whirlpool end through the first one-way valve simultaneously, plays balance two ends air pressure, to solve the series of problems such as pressure side obstruction, whirlpool end deficiency of air.
Claims (6)
1. one kind is applicable to the turbo charge system of single cylinder diesel, comprise the turbosupercharger primarily of gas compressor and turbine composition, it is characterized in that: be arranged in parallel the first identical exhausting waste gas pipeline of caliber and the second exhausting waste gas pipeline between the exhaust valve of the cylinder of described single cylinder diesel and the suction port of described turbine, the length of the second described exhausting waste gas pipeline is greater than the length of the first described exhausting waste gas pipeline;
The length difference Δ L of the second described exhausting waste gas pipeline and the first described exhausting waste gas pipeline is: Δ L=V
ex× 60/4n, wherein, V
exthe speed of the air-flow in the second exhausting waste gas pipeline described in expression and the first described exhausting waste gas pipeline, n represents the rotating speed of single cylinder diesel.
2. a kind of turbo charge system being applicable to single cylinder diesel according to claim 1, it is characterized in that: the suction port of described gas compressor is connected with air intake conduit, the air outlet of described gas compressor is connected with pressurization gas discharge conduit, between the intake valve of the air outlet of described pressurization gas discharge conduit and the cylinder of described single cylinder diesel, is provided with gas holder.
3. a kind of turbo charge system being applicable to single cylinder diesel according to claim 2, it is characterized in that: the air outlet of described gas compressor is connected by the suction port of pressurization gas flow pipe with described turbine, described pressurization gas flow pipe is provided with the first one-way valve, the air outlet of described gas compressor is connected by the suction port of pressurization gas return line with described gas compressor, and described pressurization gas return line is provided with the second one-way valve.
4. a kind of turbo charge system being applicable to single cylinder diesel according to claim 3, is characterized in that: the first described one-way valve and the second described one-way valve are pressure opening and closing valve.
5. a kind of turbo charge system being applicable to single cylinder diesel according to claim 4, is characterized in that: the air outlet of described turbine is connected with exhaust emission tube road.
6. a kind of turbo charge system being applicable to single cylinder diesel according to claim 5, it is characterized in that: the structure of the second described exhausting waste gas pipeline is flute profile, the second described exhausting waste gas pipeline comprises two lateral canals and a connecting tube, one end of side pipe described in first is communicated with one end of the first described exhausting waste gas pipeline, the other end of the side pipe described in first is communicated with one end of described connecting tube, one end of side pipe described in second is communicated with the other end of the first described exhausting waste gas pipeline, the other end of the side pipe described in second is communicated with the other end of described connecting tube.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310173924.7A CN103244258B (en) | 2013-05-13 | 2013-05-13 | A kind of turbo charge system being applicable to single cylinder diesel |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310173924.7A CN103244258B (en) | 2013-05-13 | 2013-05-13 | A kind of turbo charge system being applicable to single cylinder diesel |
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| CN103244258A CN103244258A (en) | 2013-08-14 |
| CN103244258B true CN103244258B (en) | 2015-12-16 |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104847481B (en) * | 2015-04-01 | 2017-10-27 | 武汉理工大学 | Air pressure energy storage type turbo charging installation |
| CN114483612B (en) * | 2022-03-04 | 2024-01-05 | 中国商用飞机有限责任公司 | Aerodynamic turbine compression system |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2858656A1 (en) * | 2003-08-08 | 2005-02-11 | Moteur Moderne Le | Supercharged engine for vehicle, has two turbocompression stages with high and low pressure turbines, where low pressure turbine has inlet connected to pipes by duct, and control unit preventing/allowing exhaust gas circulation in duct |
| GB2489462A (en) * | 2011-03-29 | 2012-10-03 | Gm Global Tech Operations Inc | Exhaust manifold for a two-stage turbocharger for an internal combustion engine |
| CN203362306U (en) * | 2013-05-13 | 2013-12-25 | 宁波威孚天力增压技术有限公司 | Turbocharging system applicable to single cylinder diesel engine |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2457326B (en) * | 2008-10-17 | 2010-01-06 | Univ Loughborough | An exhaust arrangement for an internal combustion engine |
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- 2013-05-13 CN CN201310173924.7A patent/CN103244258B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2858656A1 (en) * | 2003-08-08 | 2005-02-11 | Moteur Moderne Le | Supercharged engine for vehicle, has two turbocompression stages with high and low pressure turbines, where low pressure turbine has inlet connected to pipes by duct, and control unit preventing/allowing exhaust gas circulation in duct |
| GB2489462A (en) * | 2011-03-29 | 2012-10-03 | Gm Global Tech Operations Inc | Exhaust manifold for a two-stage turbocharger for an internal combustion engine |
| CN203362306U (en) * | 2013-05-13 | 2013-12-25 | 宁波威孚天力增压技术有限公司 | Turbocharging system applicable to single cylinder diesel engine |
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| CN103244258A (en) | 2013-08-14 |
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Effective date of registration: 20160802 Address after: 100000 Haidian District, Xueyuan Road, No. 37, Patentee after: Beihang University Patentee after: Ningbo Weifu Tianli Turbocharging Technology Co., Ltd. Address before: 315000 Zhejiang Province, Ningbo Jiangbei District Haichuan Road 168 Lane No. 1 Patentee before: Ningbo Weifu Tianli Turbocharging Technology Co., Ltd. |