CN107939558B - Internal combustion engine exhaust system with exhaust gas recirculation - Google Patents
Internal combustion engine exhaust system with exhaust gas recirculation Download PDFInfo
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- CN107939558B CN107939558B CN201710928487.3A CN201710928487A CN107939558B CN 107939558 B CN107939558 B CN 107939558B CN 201710928487 A CN201710928487 A CN 201710928487A CN 107939558 B CN107939558 B CN 107939558B
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- exhaust
- turbine
- volute
- turbine volute
- manifold
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 13
- 238000000034 method Methods 0.000 claims abstract 2
- 230000009286 beneficial effect Effects 0.000 abstract description 5
- 230000000694 effects Effects 0.000 abstract description 3
- 238000001816 cooling Methods 0.000 abstract description 2
- 238000012423 maintenance Methods 0.000 abstract description 2
- 239000007789 gas Substances 0.000 description 20
- 238000010586 diagram Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000021715 photosynthesis, light harvesting Effects 0.000 description 1
- 238000009991 scouring Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
- F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/30—Exhaust heads, chambers, or the like
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
- F01N13/08—Other arrangements or adaptations of exhaust conduits
- F01N13/10—Other arrangements or adaptations of exhaust conduits of exhaust manifolds
- F01N13/107—More than one exhaust manifold or exhaust collector
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
- F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
- F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/14—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the exhaust system
- F02M26/16—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the exhaust system with EGR valves located at or near the connection to the exhaust system
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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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Chemical Kinetics & Catalysis (AREA)
- General Chemical & Material Sciences (AREA)
- Exhaust-Gas Circulating Devices (AREA)
- Supercharger (AREA)
Abstract
The invention discloses an internal combustion engine exhaust system with exhaust gas recirculation, which comprises a plurality of engine cylinders, an exhaust manifold, an EGR valve, an EGR cooler, an air inlet manifold, a turbine, a supercharger compressor, a supercharging intercooler and a middle-cooling rear air inlet pipe; the method is characterized in that: a plurality of engine cylinders are connected with a plurality of exhaust manifolds in groups respectively; the turbine has a plurality of turbine volute chambers opening into a turbine wheel; a plurality of said exhaust manifolds respectively entering a corresponding plurality of said turbine volute chambers; at least part of the exhaust manifold is simultaneously connected with the EGR valve. The three-channel supercharger volute and the exhaust manifold have the advantages that the three-channel supercharger volute and the exhaust manifold are arranged to be more beneficial to reducing interference among exhaust of each cylinder, and exhaust pulse effect is utilized to facilitate maintenance of exhaust energy. The three-channel supercharger volute has the beneficial effects that the volute cavities with different sectional areas are arranged in the three-channel supercharger volute, so that different gradient volute asymmetries can be formed, and the EGR rate of the engine can be optimized under different working conditions.
Description
Technical Field
The invention belongs to the technical field of turbocharged internal combustion engines, and particularly relates to an internal combustion engine exhaust system with exhaust gas recirculation and adopting an asymmetric turbocharger.
Background
To meet engine emission requirements, the engine is provided with the proper EGR rate through an asymmetric turbocharger, an EGR valve, and an associated exhaust system.
The existing solution is mainly disclosed in patent CN104508284(a), that is, the EGR rate requirement of the engine under different operating conditions is satisfied by controlling the EGR valve through the asymmetric double-channel supercharger and the EGR valve. The disadvantage is that when the turbine volute is asymmetric to a large extent, it is difficult to generate a large exhaust gas pressure, and the EGR rate requirement can only be met by forcing the EGR valve. When the asymmetry is small, at high speed and high load, the exhaust back pressure is high, and an excessive EGR rate is generated. Daimler tends to employ greater degrees of asymmetry to meet EGR rate requirements by forcing the EGR valve during some conditions.
The main disadvantages of this solution are: 1) the three cylinders share one volute exhaust flow channel, so that exhaust energy dissipation among the cylinders is high. 2) The forced EGR valve directly bears high-temperature exhaust scouring, so that higher heat load is brought, and the reliability is poorer. Furthermore, forced EGR valves also introduce a loss of exhaust energy.
Disclosure of Invention
The invention aims to provide a turbocharger and an exhaust system of an internal combustion engine with exhaust gas recirculation, which adopts an asymmetric turbocharger, and can improve the exhaust energy utilization rate of the turbocharger as much as possible while meeting the EGR rate of the engine.
In order to achieve the purpose, the invention adopts the following technical scheme:
an internal combustion engine exhaust system with exhaust gas recirculation comprises a plurality of engine cylinders, an exhaust manifold, an EGR valve, an EGR cooler, an air inlet manifold, a turbine, a supercharger compressor, a supercharged intercooler and an intermediate-cold rear air inlet pipe; the exhaust gas of the engine cylinder partially enters the turbine through the exhaust manifold, and partially reenters the engine cylinder through the EGR valve, the EGR cooler and the intake manifold; the air inlet of the engine cylinder returns to the engine cylinder after passing through the supercharger compressor, the supercharging intercooler and the middle-cooling rear air inlet pipe, and is characterized in that: a plurality of engine cylinders are connected with a plurality of exhaust manifolds in groups respectively; the turbine has a plurality of turbine volute chambers opening into a turbine wheel; a plurality of said exhaust manifolds respectively entering a corresponding plurality of said turbine volute chambers; at least part of the exhaust manifold is simultaneously connected with the EGR valve.
It is further characterized in that: each exhaust manifold is connected with at least two engine cylinder exhaust gases.
Preferably: the number of the engine cylinders is six, every two engine cylinders are combined and connected with three exhaust manifolds, and the turbine comprises a first turbine volute cavity, a second turbine volute cavity and a third turbine volute cavity; and a first exhaust manifold of the three exhaust manifolds is simultaneously connected with the EGR valve and the first turbine volute cavity, a second exhaust manifold is simultaneously connected with the EGR valve and the second turbine volute cavity, and a third exhaust manifold is separately connected with the third turbine volute cavity.
The sectional areas of the first turbine volute cavity, the second turbine volute cavity and the third turbine volute cavity are arranged in a gradient manner.
Preferably: the sectional area of the third turbine volute cavity is larger than that of the second turbine volute cavity and the first turbine volute cavity.
The second turbine volute cavity and the third turbine volute cavity are asymmetrically arranged in cross section.
The EGR valve is a three-way valve.
The three-channel supercharger volute and the exhaust manifold have the advantages that the three-channel supercharger volute and the exhaust manifold are arranged to be more beneficial to reducing interference among exhaust of each cylinder, and exhaust pulse effect is utilized to facilitate maintenance of exhaust energy. The three-channel supercharger volute has the beneficial effects that the volute cavities with different sectional areas are arranged in the three-channel supercharger volute, so that different gradient volute asymmetries can be formed, and the EGR rate of the engine can be optimized under different working conditions.
Drawings
FIG. 1 is a schematic diagram of an engine system architecture of the present invention.
Fig. 2 is a schematic view of a turbine volute cavity structure of the turbine of the present invention.
FIG. 3 is a schematic view of a second turbine volute cavity structure according to the present invention.
FIG. 4 is a schematic view of a third turbine volute cavity configuration according to the present invention.
FIGS. 5-9 are schematic views of states of the EGR valve under different operating conditions.
Detailed Description
As shown in fig. 1, an exhaust system of an internal combustion engine with exhaust gas recirculation using an asymmetric turbocharger includes a plurality of engine cylinders, an exhaust manifold, an EGR valve 20, an EGR cooler 19, an EGR-cooled pipe 18, an intake manifold 17, a turbine, a supercharger compressor 28, a supercharge intercooler 29, and a middle-cooled intake pipe 30; the exhaust gases of the engine cylinders partly enter the turbine via the exhaust manifold and partly re-enter the engine cylinders via the EGR valve 20, the EGR cooler 19, the intake manifold 17. The gases exiting the first 11 and second 12 cylinders of the engine cylinder are directed into a first exhaust manifold 21; the gas discharged from the third cylinder 13 and the fourth cylinder 14 is introduced into the second exhaust manifold 22; the gases from the fifth cylinder 15 and the sixth cylinder 16 are directed to a third exhaust manifold 23. The gases exiting the second exhaust manifold 22 and the third exhaust manifold 23 are at least partially recirculated to the intake manifold 17. The gas in the first exhaust manifold 21, the second exhaust manifold 22 and the third exhaust manifold 23 is respectively sent into a first turbine volute cavity 24, a second turbine volute cavity 25 and a third turbine volute cavity 26 of the turbine, and then the turbine impeller 27 is pushed.
As shown in fig. 2, the above-mentioned asymmetric turbocharger comprises a turbine including a volute and a turbine blade 31 portion. Three volute chambers are provided in the turbine volute, a first turbine volute chamber 24, a second turbine volute chamber 25, and a third turbine volute chamber 26. The three volute cavities are respectively connected with three groups of different exhaust manifolds. Wherein the third turbine volute chamber 26 has a larger cross-sectional area than the first turbine volute chamber 24 and the second turbine volute chamber 25. Wherein a part of the gas entering the first exhaust manifold 21 and the second exhaust manifold 22 is recirculated by EGR, and the rest enters the first turbine volute cavity 24 and the second turbine volute cavity 25 of the turbine respectively. Compared with the prior art, the volute cavity 25 and the volute cavity 24 with different asymmetry degrees are arranged relative to the volute cavity 26. The asymmetric flow channel is more beneficial to forming the EGR rate with different gradients, and the EGR rate of the engine under different working conditions is convenient to optimize.
With the structure shown in fig. 2, the following effects can be produced. Three groups of exhaust manifolds of the engine are respectively connected with a first turbine volute cavity 24, a second turbine volute cavity 25 and a third turbine volute cavity 26. Enters the turbine through the volute cavity to do work through expansion. Because the first turbine volute cavity 24, the second turbine volute cavity 25 and the third turbine volute cavity 26 have different throat areas, airflow in the three sets of volute cavities is throttled to different degrees. The throttling of the airflow received by the third turbine volute chamber 26 is small, so that the gas energy in the third turbine volute chamber 26 is kept better, the gas pressure is low, and the high working efficiency of the turbine can be ensured. The throat areas of the first turbine volute cavity 24, the second turbine volute cavity 25 and the third turbine volute cavity 26 are increased in sequence. Under the influence of the throttling action, the pressures of the first, second and third turbine volute chambers 24, 25, 26 decrease in sequence. The first and second turbine volute chambers 24, 25 have a higher pressure than the third turbine volute chamber 26 and therefore form a suitable pressure gradient with respect to the pressurised inlet air. This facilitates the use of a hot-end EGR valve to provide the desired EGR rate for the engine. Further, the first turbine volute chamber 24 has a smaller throat area relative to the second turbine volute chamber 25, and therefore, is capable of creating a greater pressure gradient relative to the supercharged inlet air. It is convenient to provide a smaller amount of exhaust gas recirculation at low engine speed conditions. When the engine needs a larger amount of EGR, part of the exhaust gas in the first and second exhaust manifolds 21 and 22 can be introduced into the EGR cooler through the EGR line while utilizing the pressure difference formed by the first and second turbo casing cavities 24 and 25.
FIGS. 5-9 are schematic views of states of the EGR valve under different operating conditions.
When the engine is operating at low speed and high load, the engine requires a lower EGR rate, as shown in fig. 9, where the EGR valve plate 36 closes the second flow passage 35, the first flow passage 34 opens, and EGR enters the intake manifold 17 through the EGR cooler 19. When the engine is operating at low speed and low load, and a high EGR rate is required, the EGR valve plate 36 partially or fully opens the second flow passage 35 and the first flow passage 34, as shown in fig. 6 and 7. When the engine requires a medium EGR rate, the EGR valve plate 36 partially opens the second flow passage 35, or the EGR valve plate 36 closes the first flow passage 34, as shown in fig. 5 and 8.
It is also possible in the present invention to provide that the second volute chamber 25 is smaller than the first turbine volute chamber 24, as shown in figure 3. Or as shown in fig. 4, the asymmetric turbocharger comprises a turbine including a volute and turbine blade 31 portion. Three volute chambers are provided in the turbine volute, a first turbine volute chamber 24, a second turbine volute chamber 25, and a third turbine volute chamber 26. The three volute cavities are respectively connected with three groups of different exhaust manifolds. Wherein the turbine volute second volute chamber 25 has a larger cross-sectional area relative to the first and third turbine volute chambers 24, 26. Wherein a part of the gas entering the first exhaust manifold 21 and the second exhaust manifold 22 is recirculated by EGR, and the rest enters the first turbine volute cavity 24 and the third turbine volute cavity 26 of the turbine respectively.
The invention has been described above, it is obvious that the specific implementation of the invention is not limited to the above-described manner, and it is within the scope of the invention to apply the inventive concept and solution to other applications without substantial or substantial modification.
Claims (5)
1. An internal combustion engine exhaust system with exhaust gas recirculation comprises a plurality of engine cylinders, an exhaust manifold, an EGR valve, an EGR cooler, an air inlet manifold, a turbine, a supercharger compressor, a supercharged intercooler and an intermediate-cold rear air inlet pipe; the exhaust gas of the engine cylinder partially enters the turbine through the exhaust manifold, and partially reenters the engine cylinder through the EGR valve, the EGR cooler and the intake manifold; the method is characterized in that: a plurality of engine cylinders are connected with a plurality of exhaust manifolds in groups respectively; the turbine has a plurality of turbine volute chambers opening into a turbine wheel; a plurality of said exhaust manifolds respectively entering a corresponding plurality of said turbine volute chambers; at least part of the exhaust manifold is simultaneously connected with the EGR valve;
each exhaust manifold is connected with at least two engine cylinder exhausts;
the number of the engine cylinders is six, every two engine cylinders are combined and connected with three exhaust manifolds, and the turbine comprises a first turbine volute cavity, a second turbine volute cavity and a third turbine volute cavity; and a first exhaust manifold of the three exhaust manifolds is simultaneously connected with the EGR valve and the first turbine volute cavity, a second exhaust manifold is simultaneously connected with the EGR valve and the second turbine volute cavity, and a third exhaust manifold is separately connected with the third turbine volute cavity.
2. An internal combustion engine exhaust system with exhaust gas recirculation according to claim 1, characterized in that: the sectional areas of the first turbine volute cavity, the second turbine volute cavity and the third turbine volute cavity are arranged in a gradient manner.
3. An internal combustion engine exhaust system with exhaust gas recirculation according to claim 2, characterized in that: the sectional area of the third turbine volute cavity is larger than that of the second turbine volute cavity and the first turbine volute cavity.
4. An internal combustion engine exhaust system with exhaust gas recirculation according to claim 3, characterized in that: the second turbine volute cavity and the third turbine volute cavity are asymmetrically arranged in cross section.
5. An internal combustion engine exhaust system with exhaust gas recirculation according to any one of claims 1 to 4, characterized in that: the EGR valve is a three-way valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710928487.3A CN107939558B (en) | 2017-10-09 | 2017-10-09 | Internal combustion engine exhaust system with exhaust gas recirculation |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710928487.3A CN107939558B (en) | 2017-10-09 | 2017-10-09 | Internal combustion engine exhaust system with exhaust gas recirculation |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107939558A CN107939558A (en) | 2018-04-20 |
| CN107939558B true CN107939558B (en) | 2019-12-31 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201710928487.3A Active CN107939558B (en) | 2017-10-09 | 2017-10-09 | Internal combustion engine exhaust system with exhaust gas recirculation |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111042954A (en) * | 2019-12-05 | 2020-04-21 | 一汽解放汽车有限公司 | Exhaust heating system of internal combustion engine |
| CN112211757A (en) * | 2020-10-14 | 2021-01-12 | 哈尔滨工程大学 | Supercharged diesel engine EGR rate flexible adjustable system and adjusting method |
| CN113217233B (en) * | 2021-05-07 | 2022-04-26 | 潍柴动力股份有限公司 | Engine exhaust gas circulation system and engine misfire judging method |
| CN117090716B (en) * | 2023-10-19 | 2024-01-12 | 潍柴动力股份有限公司 | Variable pulse conversion valve, control method thereof and engine |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4179892A (en) * | 1977-12-27 | 1979-12-25 | Cummins Engine Company, Inc. | Internal combustion engine with exhaust gas recirculation |
| US4395884A (en) * | 1981-02-26 | 1983-08-02 | The Jacobs Manufacturing Company | Method and apparatus for improved engine braking and operation |
| US7311090B2 (en) * | 2006-01-31 | 2007-12-25 | International Engine Intellectual Property Company, Llc | Engine exhaust gas passage flow orifice and method |
| DE202014100235U1 (en) * | 2014-01-20 | 2014-02-10 | Ford Global Technologies, Llc | Internal combustion engine with double-flow axial turbine and grouped cylinders |
| CN103953400A (en) * | 2014-03-04 | 2014-07-30 | 大同北方天力增压技术有限公司 | Turbine volute structure meeting requirement for containing booster |
-
2017
- 2017-10-09 CN CN201710928487.3A patent/CN107939558B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4179892A (en) * | 1977-12-27 | 1979-12-25 | Cummins Engine Company, Inc. | Internal combustion engine with exhaust gas recirculation |
| US4395884A (en) * | 1981-02-26 | 1983-08-02 | The Jacobs Manufacturing Company | Method and apparatus for improved engine braking and operation |
| US7311090B2 (en) * | 2006-01-31 | 2007-12-25 | International Engine Intellectual Property Company, Llc | Engine exhaust gas passage flow orifice and method |
| DE202014100235U1 (en) * | 2014-01-20 | 2014-02-10 | Ford Global Technologies, Llc | Internal combustion engine with double-flow axial turbine and grouped cylinders |
| CN103953400A (en) * | 2014-03-04 | 2014-07-30 | 大同北方天力增压技术有限公司 | Turbine volute structure meeting requirement for containing booster |
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| CN107939558A (en) | 2018-04-20 |
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