CN113530665A - Two-stage supercharging system and method for diesel engine - Google Patents
Two-stage supercharging system and method for diesel engine Download PDFInfo
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- CN113530665A CN113530665A CN202110979854.9A CN202110979854A CN113530665A CN 113530665 A CN113530665 A CN 113530665A CN 202110979854 A CN202110979854 A CN 202110979854A CN 113530665 A CN113530665 A CN 113530665A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/004—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust drives arranged in series
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/16—Control of the pumps by bypassing charging air
- F02B37/162—Control of the pumps by bypassing charging air by bypassing, e.g. partially, intake air from pump inlet to pump outlet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
- F02B37/183—Arrangements of bypass valves or actuators therefor
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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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- Engineering & Computer Science (AREA)
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- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
Abstract
The invention relates to the technical field of engines, in particular to a two-stage supercharging system and a supercharging method for a diesel engine, wherein the two-stage supercharging system for the diesel engine comprises a low-pressure stage supercharger, a high-pressure stage supercharger and a control unit, wherein the low-pressure stage supercharger comprises a low-pressure stage compressor and a low-pressure stage turbine which are connected in series, the low-pressure stage compressor is connected with an air inlet bypass valve in parallel, and the low-pressure stage turbine is connected with a first waste gas bypass valve in parallel; the high-pressure stage supercharger comprises a high-pressure stage compressor and a high-pressure stage turbine, and the high-pressure stage turbine is connected with a second waste gas bypass valve in parallel; the control unit is capable of controlling the intake bypass valve, the first wastegate valve, and the second wastegate valve. The control unit controls the opening and closing of the air inlet bypass valve and the first waste gas bypass valve, free switching between single-stage supercharging and two-stage supercharging is achieved, supercharging pressure of the diesel engine is accurately controlled, the full-load operation working condition of the diesel engine can be matched, and meanwhile the opening degree of the second waste gas bypass valve is controlled through the control unit, and the supercharging pressure is adjustable.
Description
Technical Field
The invention relates to the technical field of engines, in particular to a two-stage supercharging system and a two-stage supercharging method for a diesel engine.
Background
With the stricter regulations on oil consumption and emission, the requirements on the turbocharging system of the diesel engine are higher and higher. The existing traditional single-stage turbocharger cannot be well matched with the full-load operation condition of the diesel engine, and the supercharging pressure ratio is lower, so that the requirement of the modern diesel engine is more and more difficult to meet. The existing two-stage supercharging system can meet the high-speed requirement of the diesel engine by matching a high-pressure stage supercharger with the low-speed performance of the diesel engine and matching a low-pressure stage supercharger, but the supercharging pressure is not adjustable.
Disclosure of Invention
The invention aims to provide a two-stage supercharging system and a supercharging method for a diesel engine, which can be matched with the full-load operation working condition of the diesel engine and can realize high supercharging pressure and adjustable supercharging pressure.
In order to achieve the purpose, the invention adopts the following technical scheme:
a two-stage supercharging system for a diesel engine, comprising:
the low-pressure stage supercharger comprises a low-pressure stage compressor and a low-pressure stage turbine, the low-pressure stage compressor is connected with an air inlet bypass valve in parallel, and the low-pressure stage turbine is connected with a first waste gas bypass valve in parallel;
the high-pressure stage supercharger is connected with the low-pressure stage supercharger in series, the high-pressure stage supercharger comprises a high-pressure stage compressor and a high-pressure stage turbine, and the high-pressure stage turbine is connected with a second waste gas bypass valve in parallel;
a control unit for controlling the intake bypass valve, the first wastegate valve, and the second wastegate valve.
Preferably, a high-pressure stage actuator is arranged between the high-pressure stage compressor and the high-pressure stage turbine of the high-pressure stage supercharger.
Preferably, a first-stage intercooler is arranged between the low-pressure stage compressor and the high-pressure stage compressor.
Preferably, a two-stage intercooler is arranged between the high-pressure stage compressor and the diesel engine to be supercharged.
Preferably, the intake bypass valve and the first wastegate valve have only two states of opening and closing.
Preferably, the second wastegate valve can achieve stepless adjustment.
Preferably, the high-pressure stage supercharger is a variable-section turbocharger.
Preferably, the high-pressure stage supercharger is an electromechanical coupling supercharger with an electric motor.
A method for supercharging a diesel engine by using the two-stage supercharging system of the diesel engine, which comprises the following steps:
judging the current operation load of the diesel engine;
if the diesel engine is in a low-load operation region, the control unit controls the first waste gas bypass valve and the intake bypass valve to be opened and controls the second waste gas bypass valve to be closed;
if the diesel engine is in a medium-load operation area, the control unit controls the first waste gate valve, the air inlet bypass valve and the second waste gate valve to be closed;
and if the diesel engine is in a high-load operation area, the control unit controls the first waste gas bypass valve and the air inlet bypass valve to be closed and controls the opening degree of the second waste gas bypass valve.
Preferably, if the diesel engine is in a medium load operation region, the pressure ratio distribution between the high-pressure stage supercharger and the low-pressure stage supercharger is realized by adjusting the high-pressure stage actuator.
The invention has the beneficial effects that: the invention realizes the free switching of single-stage supercharging and two-stage supercharging by arranging the high-pressure-stage supercharger and the low-pressure-stage supercharger which are connected in series, arranging the air inlet bypass valve on the bypass pipeline of the low-pressure-stage compressor of the low-pressure-stage supercharging, arranging the first waste gas bypass valve on the bypass pipeline of the low-pressure-stage turbine, controlling the opening and closing of the air inlet bypass valve and the first waste gas bypass valve by the control unit, accurately controlling the supercharging pressure of the diesel engine, matching the full-load operation working condition of the diesel engine, arranging the second waste gas bypass valve on the bypass pipeline of the high-pressure-stage turbine of the high-pressure-stage supercharger, and controlling the opening degree of the second waste gas bypass valve by the control unit to realize the adjustment of the supercharging pressure.
Drawings
FIG. 1 is a schematic diagram of a two-stage supercharging system of a diesel engine provided by the present invention;
fig. 2 is a schematic view of the operating region of the diesel engine of the present invention.
In the figure:
1. a low-pressure stage supercharger; 11. a low-pressure stage compressor; 111. an intake bypass valve; 12. a low pressure stage turbine; 121. a first wastegate valve;
2. a high-pressure stage supercharger; 21. a high-pressure stage compressor; 22. a high pressure stage turbine; 221. a second wastegate valve; 23. a high-pressure stage actuator;
3. a control unit;
4. a first-stage intercooler;
5. a second-stage intercooler;
6. a diesel engine.
Detailed Description
The technical scheme of the invention is further explained by combining the attached drawings and the embodiment. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting of the invention. It should be further noted that, for the convenience of description, only some but not all of the elements associated with the present invention are shown in the drawings.
In the description of the present invention, it should be noted that unless otherwise explicitly stated or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection or a removable connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the present invention, unless otherwise expressly stated or limited, "above" or "below" a first feature means that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact with each other via another feature therebetween. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.
With the continuous tightening of oil consumption and emission regulations, the requirements on the turbocharging technology of the diesel engine 6 are higher and higher. For the traditional single-stage turbocharging technology, a compressor impeller and a turbine impeller are coaxial, and waste gas drives the turbine impeller so as to drive the compressor impeller to generate supercharging pressure, but the supercharging pressure cannot be well matched with the full-load operation condition of the diesel engine 6, and the supercharging pressure ratio is low; for the traditional asymmetric supercharging technology, a turbine is an asymmetric double-flow passage, high supercharging pressure is generated through a small flow passage, and exhaust gas bypass is realized through a large flow passage, so that although the supercharging pressure can be improved to a certain degree, increasingly strict emission requirements cannot be met; for the variable cross-section turbocharging technology, the angle of the turbine guide vane is adjustable, the flow and the flow speed of the waste gas flowing through the turbine vane can be controlled, the rotation speed of the turbine can be adjusted, and the aim of adjusting the turbocharging pressure is finally fulfilled; although the existing two-stage supercharging system can provide larger supercharging pressure, the supercharging pressure is not adjustable, and certain defects still exist.
The embodiment relates to the technical field of engines, and provides a two-stage supercharging system of a diesel engine, which comprises a low-pressure-stage supercharger 1 and a high-pressure-stage supercharger 2 which are connected in series, and a control unit 3, wherein the high-pressure-stage supercharger 2 is matched with the low-speed performance of the diesel engine 6, the low-pressure-stage supercharger 1 is matched with the high-speed demand of the diesel engine 6, and meanwhile, the oil consumption and the emission of the diesel engine 6 can be effectively reduced by the high supercharging ratio realized by two-stage supercharging.
The low-pressure stage supercharger 1 comprises a low-pressure stage compressor 11 and a low-pressure stage turbine 12 coaxial with the low-pressure stage compressor 11, wherein the low-pressure stage compressor 11 is connected with an air inlet bypass valve 111 in parallel, and the low-pressure stage turbine 12 is connected with a first waste gas bypass valve 121 in parallel. The intake bypass valve 111 and the first waste gate valve 121 are both only in an opening state and a closing state, and the control unit 3 can control the intake bypass valve 111 and the first waste gate valve 121 to be in the opening state or the closing state, so that the free switching of single-stage supercharging and two-stage supercharging is realized, the supercharging pressure of the diesel engine 6 is accurately controlled, and the full-load operation working condition of the diesel engine 6 is matched.
And the high-pressure stage supercharger 2 includes a high-pressure stage compressor 21 and a high-pressure stage turbine 22 coaxial with the high-pressure stage compressor 21, and the high-pressure stage turbine 22 is connected in parallel with a second wastegate valve 221. The second wastegate valve 221 can achieve stepless regulation, that is, the control unit 3 can control the opening degree of the second wastegate valve 221, thereby achieving regulation of the boost pressure. Preferably, the high-pressure stage supercharger 2 provided by the embodiment is a variable-section turbocharger, the variable-section turbocharger can adjust the supercharging pressure by changing the sectional area of the nozzle outlet, when the sectional area of the nozzle outlet is reduced, the exhaust flow speed of the nozzle outlet is increased, the rotating speed of the high-pressure stage turbine 22 is increased, and the supercharging pressure is correspondingly increased; conversely, as the nozzle exit cross-sectional area increases, the nozzle exit exhaust flow rate decreases, the high pressure stage turbine 22 speed decreases, and the boost pressure decreases accordingly. In other embodiments, the high-voltage stage booster 2 may be an electromechanical coupling booster with a motor, without limitation.
Further, the high-pressure stage supercharger 2 further comprises a high-pressure stage actuator 23, the high-pressure stage actuator 23 is arranged between the high-pressure stage compressor 21 and the high-pressure stage turbine 22, and when only the high-pressure stage supercharger 2 works and performs single-stage supercharging on the diesel engine 6, the control unit 3 improves the efficiency of the high-pressure stage supercharger 2 by controlling the high-pressure stage actuator 23, so that the transient responsiveness of the high-pressure stage supercharger 2 is improved; when the high-pressure-stage supercharger 2 and the low-pressure-stage supercharger 1 work simultaneously to perform two-stage supercharging on the diesel engine 6, the control unit 3 can control the high-pressure-stage actuator 23 to realize the supercharging ratio distribution between the high-pressure-stage supercharger 2 and the low-pressure-stage supercharger 1, and improve the efficiency of the high-pressure-stage supercharger 2 and the low-pressure-stage supercharger 1.
Further, a first-stage intercooler 4 is arranged between the low-pressure stage compressor 11 and the high-pressure stage compressor 21, and the temperature of air compressed by the low-pressure stage compressor 11 is reduced by the first-stage intercooler 4, so that the heat load of the diesel engine 6 is reduced, the charging efficiency of the diesel engine 6 is improved, and the power of the diesel engine 6 is further improved.
Furthermore, a two-stage intercooler 5 is arranged between the high-pressure stage compressor 21 and the diesel engine 6, and the temperature of the air compressed by the high-pressure stage compressor 21 is reduced by the two-stage intercooler 5, so that the heat load of the diesel engine 6 is reduced, the charging efficiency of the diesel engine 6 is further improved, and the power of the diesel engine 6 is improved.
The embodiment also provides a diesel engine supercharging method, which uses the diesel engine two-stage supercharging system, and comprises the following steps:
judging the current operation load of the diesel engine 6;
if the diesel engine 6 is in the low-load operation region, the control unit 3 controls the first waste gate valve 121 and the intake gate valve 111 to be opened, and controls the second waste gate valve 221 to be closed;
if the diesel engine 6 is in the intermediate load operation region, the control unit 3 controls the first wastegate valve 121, the intake bypass valve 111, and the second wastegate valve 221 to be closed;
when the diesel engine 6 is in the high load operation region, the control unit 3 controls the first wastegate valve 121 and the intake bypass valve 111 to be closed, and controls the opening degree of the second wastegate valve 221.
Specifically, as shown in fig. 2, when the diesel engine 6 is in the low load region (region a), the control unit 3 of the diesel engine 6 controls the intake bypass valve 111 to be opened, the first wastegate valve 121 to be opened, and the second wastegate valve 221 to be closed, and at this time, the intake and exhaust gases only flow through the high-pressure-stage supercharger 2, and the high-pressure-stage supercharger 2 in the low load region (region a) can operate efficiently by matching the small high-pressure-stage turbine 22 and the high-pressure-stage compressor 21 and adjusting the high-pressure-stage actuator 23, and at the same time, the small high-pressure-stage supercharger 2 can improve the responsiveness of the transient state.
When the diesel engine 6 is in the intermediate load region (B region), the control unit 3 of the diesel engine 6 controls the intake bypass valve 111 to be closed, the first wastegate valve 121 to be closed, and the second wastegate valve 221 to be closed, thereby achieving two-stage supercharging. The pressure ratio distribution between the high-pressure-stage supercharger 2 and the low-pressure-stage supercharger 1 is realized by adjusting the high-pressure-stage actuator 23.
When the diesel engine 6 is in the high load region (region C), the control unit 3 of the diesel engine 6 controls the intake bypass valve 111 to be closed, the first wastegate valve 121 to be closed, and the opening degree of the second wastegate valve 221 to be adjusted, thereby avoiding the overspeed risk of the high-pressure-stage supercharger 2 due to an excessively high supercharging pressure.
The diesel engine supercharging method provided by the embodiment can realize free switching of single-stage supercharging and two-stage supercharging according to the current running load of the diesel engine, namely, single-stage supercharging is realized at low load, two-stage supercharging is realized at medium and high load, the supercharging pressure of the diesel engine 6 can be accurately controlled, and the diesel engine supercharging method has remarkable effects of improving the EGR rate of the diesel engine 6 and reducing emission.
It should be understood that the above-described embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the embodiments of the present invention. Other variations and modifications will be apparent to persons skilled in the art in light of the above description. And are neither required nor exhaustive of all embodiments. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present invention should be included in the protection scope of the claims of the present invention.
Claims (10)
1. A two-stage supercharging system for a diesel engine, comprising:
the low-pressure stage supercharger (1) comprises a low-pressure stage compressor (11) and a low-pressure stage turbine (12), wherein the low-pressure stage compressor (11) is connected with an air inlet bypass valve (111) in parallel, and the low-pressure stage turbine (12) is connected with a first waste gas bypass valve (121) in parallel;
the high-pressure stage supercharger (2) is connected with the low-pressure stage supercharger (1) in series, the high-pressure stage supercharger (2) comprises a high-pressure stage compressor (21) and a high-pressure stage turbine (22), and the high-pressure stage turbine (22) is connected with a second waste gas bypass valve (221) in parallel;
a control unit (3), the control unit (3) being configured to control the intake bypass valve (111), the first wastegate valve (121), and the second wastegate valve (221).
2. A two-stage supercharging system according to claim 1, characterized in that a high-pressure stage actuator (23) is provided between the high-pressure stage compressor (21) and the high-pressure stage turbine (22) of the high-pressure stage supercharger (2).
3. Two-stage supercharging system according to claim 2, characterized in that a one-stage intercooler (4) is provided between the low-pressure stage compressor (11) and the high-pressure stage compressor (21).
4. Two-stage supercharging system according to claim 2, characterized in that a two-stage intercooler (5) is provided between the high-pressure stage compressor (21) and the diesel engine (6) to be supercharged.
5. A two-stage supercharging system according to claim 1, characterized in that the intake bypass valve (111) and the first wastegate valve (121) are opened and closed only in two states.
6. A two-stage supercharging system according to claim 1, characterized in that the second wastegate valve (221) can be adjusted steplessly.
7. A two-stage supercharging system according to any of claims 1 to 6, characterized in that the high-pressure stage supercharger (2) is a variable-area turbocharger.
8. A two-stage supercharging system according to any of claims 1 to 6, characterized in that the high-pressure stage supercharger (2) is an electromechanical coupling supercharger with an electric motor.
9. A method for supercharging a diesel engine (6), characterized by using a two-stage supercharging system for a diesel engine according to any of claims 1 to 8, comprising the steps of:
judging the current operation load of the diesel engine (6);
if the diesel engine (6) is in a low-load operation region, the control unit (3) controls the first waste gate valve (121) and the intake bypass valve (111) to be opened, and controls the second waste gate valve (221) to be closed;
if the diesel engine (6) is in a medium load operation region, the control unit (3) controls the first waste gate valve (121), the intake bypass valve (111) and the second waste gate valve (221) to be closed;
if the diesel engine (6) is in a high-load operation region, the control unit (3) controls the first waste gate valve (121) and the intake bypass valve (111) to be closed, and controls the opening degree of the second waste gate valve (221).
10. Method for supercharging a diesel engine (6) according to claim 9, characterized in that the pressure ratio distribution between the high-pressure stage supercharger (2) and the low-pressure stage supercharger (1) is achieved by adjusting a high-pressure stage actuator (23) if the diesel engine (6) is in a medium-load operating region.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202110979854.9A CN113530665B (en) | 2021-08-25 | 2021-08-25 | Two-stage supercharging system and method for diesel engine |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202110979854.9A CN113530665B (en) | 2021-08-25 | 2021-08-25 | Two-stage supercharging system and method for diesel engine |
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102333941A (en) * | 2009-02-27 | 2012-01-25 | 三菱重工业株式会社 | Supercharging system for internal combustion engine |
| CN103233825A (en) * | 2013-04-07 | 2013-08-07 | 中国人民解放军军事交通学院 | Secondary adjustable boosting control system and control method thereof |
| CN105386857A (en) * | 2015-11-27 | 2016-03-09 | 吉林大学 | Internal combustion engine two-stage pressurization control system and control method thereof |
| CN105781716A (en) * | 2016-03-22 | 2016-07-20 | 吉林大学 | Electric-assistance variable nozzle turbocharging system and control method thereof |
-
2021
- 2021-08-25 CN CN202110979854.9A patent/CN113530665B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102333941A (en) * | 2009-02-27 | 2012-01-25 | 三菱重工业株式会社 | Supercharging system for internal combustion engine |
| CN103233825A (en) * | 2013-04-07 | 2013-08-07 | 中国人民解放军军事交通学院 | Secondary adjustable boosting control system and control method thereof |
| CN105386857A (en) * | 2015-11-27 | 2016-03-09 | 吉林大学 | Internal combustion engine two-stage pressurization control system and control method thereof |
| CN105781716A (en) * | 2016-03-22 | 2016-07-20 | 吉林大学 | Electric-assistance variable nozzle turbocharging system and control method thereof |
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