CN107701297B - Piston type pulse energy delayed release turbocharging device - Google Patents
Piston type pulse energy delayed release turbocharging device Download PDFInfo
- Publication number
- CN107701297B CN107701297B CN201710969290.4A CN201710969290A CN107701297B CN 107701297 B CN107701297 B CN 107701297B CN 201710969290 A CN201710969290 A CN 201710969290A CN 107701297 B CN107701297 B CN 107701297B
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- Prior art keywords
- buffer
- piston
- cylinder
- exhaust
- exhaust manifold
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Classifications
-
- 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
- F02B37/22—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits
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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
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
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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)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
- Characterised By The Charging Evacuation (AREA)
Abstract
The invention discloses a piston type pulse energy delayed release turbocharging device, which comprises a crankshaft, a cylinder, a turbine and an exhaust manifold, wherein the crankshaft is in transmission connection with a piston in the cylinder; wherein, still include: the first end of the buffer cylinder is communicated with the exhaust manifold, and the second end of the buffer cylinder is communicated with the turbine rear exhaust pipe through a bypass pipe; the control valve is arranged at the joint of the buffer cylinder and the exhaust manifold; the buffer piston is slidably arranged in the buffer cylinder; the push rod passes through the second end of the buffer cylinder and is communicated with the buffer piston; the invention has compact structure, small occupied space, serialization production and convenient disassembly and assembly, and is suitable for variable turbine supercharging systems with various cylinder numbers.
Description
Technical Field
The invention relates to the technical field of turbocharging, in particular to a piston type pulse energy delayed release turbocharging device.
Background
The variable turbocharging system can effectively relieve the contradiction between the high working condition and the low working condition of the diesel engine matched with the supercharger, and improve the dynamic property and the fuel economy of the low-rotation-speed working condition of the diesel engine. When the variable turbocharging system such as the sequential turbocharging, the two-stage adjustable turbocharging or the variable geometry turbocharging is applied to the diesel engine, under the working condition of low rotating speed of the diesel engine, the equivalent nozzle ring area is smaller, so that a strong reflection effect is formed on exhaust pressure pulse, the exhaust pressure pulse is too high, the energy consumed by a piston for pushing exhaust gas out of a cylinder is increased, the pulse energy loss is also increased, and the fuel consumption of the diesel engine is increased.
The invention 200810203054.2, the invention 200810203055.7 and the invention 200920210502.1 propose variable exhaust pipe system schemes, the turbocharger system is switched between pulse supercharging and constant pressure supercharging (or quasi-constant pressure supercharging) through a control valve, and the requirements of high and low working conditions can be considered.
Disclosure of Invention
The invention aims to provide a piston type pulse energy delayed release turbocharging system, which can effectively reduce the excessive pressure pulse amplitude caused by excessively small turbine equivalent flow area, reduce the resistance of an exhaust system and fully utilize the pulse energy of exhaust when a diesel engine runs at a low speed.
The invention provides a piston type pulse energy delayed release turbocharging device, which comprises a crankshaft, a cylinder, a turbine and an exhaust manifold, wherein the crankshaft is in transmission connection with a piston in the cylinder;
wherein, still include:
the first end of the buffer cylinder is communicated with the exhaust manifold, and the second end of the buffer cylinder is communicated with the turbine rear exhaust pipe through a bypass pipe;
the control valve is arranged at the joint of the buffer cylinder and the exhaust manifold;
a cushion piston slidably disposed within the cushion cylinder;
the push rod passes through the second end of the buffer cylinder and is connected with the buffer piston; the push rod is used for pulling the buffer piston to move towards the second end of the buffer cylinder in the middle pressure wave crest period of free exhaust and pushing the buffer piston to move towards the first end of the buffer cylinder in the pressure wave trough period of forced exhaust.
The piston type pulse energy delayed release turbocharger as described above, preferably further comprises a clutch and a transmission mechanism, wherein a first end of the transmission mechanism is in transmission connection with the crankshaft through the clutch, and a second end of the transmission mechanism is connected with the push rod.
The piston type pulse energy delayed release turbocharger as described above, wherein preferably the transmission mechanism includes a first pulley, a second pulley, a buffer crank and a buffer link;
the first belt pulley is in transmission connection with the clutch, and the first belt pulley is connected with the second belt pulley through a belt; the first end of the buffer crank is connected with the second belt wheel, the second end of the buffer crank is hinged with the first end of the buffer connecting rod, and the second end of the buffer connecting rod is hinged with one end of the push rod, which is positioned outside the buffer cylinder.
The piston type pulse energy delayed release turbocharger as described above, wherein preferably, the first pulley and the second pulley are both toothed pulleys, and the belt is a toothed belt.
The piston type pulse energy delayed release turbocharger as described above, wherein the transmission ratio between the first pulley and the second pulley is preferably half the number of cylinders connected to the exhaust manifold.
The piston type pulse energy delayed release turbocharger as described above, wherein the pushrod is preferably slidably and sealingly connected to the buffer cylinder.
The piston type pulse energy delayed release turbocharger as described above, wherein the buffer cylinder is preferably slidably and sealingly connected to the buffer piston.
Compared with the prior art, the control valve is opened under the low-speed steady-state working condition of the engine; in the middle stage of free exhaust, the valve exhaust speed is high, the push rod pulls the buffer piston to move towards the second end of the buffer cylinder, the pressure of an exhaust manifold caused by high-speed exhaust is reduced, the exhaust speed is low at the end of forced exhaust, the buffer piston moves towards the first end of the buffer cylinder, the pressure of the exhaust manifold is improved, the piston is circularly reciprocated, the fluctuation range of the pressure in the exhaust manifold is reduced, the pumping loss of the exhaust of the cylinder is reduced, the pressure of a turbine inlet is relatively stable, and the turbine efficiency is improved.
When the engine is in a high-speed working condition, the control valve is closed, the push rod is controlled to stop moving, the exhaust pipe system works in a conventional exhaust pipe system, at the moment, the actual effective flow area of the variable turbine is larger, the reflection of pressure waves is weaker, the pressure fluctuation range in the exhaust pipe cannot be too high, and the exhaust pipe can keep enough boost pressure due to the fact that the air flow flowing through the engine is larger, so that the boost system has good transient performance.
The invention has compact structure, small occupied space, serialization production and convenient disassembly and assembly, and is suitable for variable turbine supercharging systems with various cylinder numbers.
Drawings
Fig. 1 is a schematic structural view of the present invention.
Reference numerals illustrate:
the engine comprises a crankshaft, a 2-cylinder, a 3-turbine, a 4-exhaust manifold, a 5-bypass pipe, a 6-turbine rear exhaust pipe, a 7-control valve, an 8-buffer piston, a 9-push rod, a 10-clutch, an 11-first belt pulley, a 12-second belt pulley, a 13-buffer crank, a 14-buffer connecting rod, a 15-belt and a 16-buffer cylinder.
Detailed Description
The embodiments described below by referring to the drawings are illustrative only and are not to be construed as limiting the invention.
Referring to fig. 1, fig. 1 is a schematic structural diagram of the present invention. The specific embodiment of the invention provides a piston type pulse energy delayed release turbocharging device, which comprises a crankshaft 1, a cylinder 2, a turbine 3 and an exhaust manifold 4, wherein the crankshaft 1 is in transmission connection with a piston in the cylinder 2, the exhaust manifold 4 is used for being communicated with the cylinder 2 during exhaust, an exhaust gas inlet of the turbine 3 is communicated with the exhaust manifold 4, and an exhaust gas outlet of the turbine 3 is provided with a turbine rear exhaust pipe 6; wherein, still include:
a buffer cylinder 16, wherein a first end of the buffer cylinder 16 is communicated with the exhaust manifold 4, and a second end of the buffer cylinder 16 is communicated with the turbine rear exhaust pipe 6 through a bypass pipe 5;
a control valve 7, wherein the control valve 7 is arranged at the joint of the buffer cylinder 16 and the exhaust manifold 4;
a cushion piston 8, the cushion piston 8 being slidably disposed within the cushion cylinder 16;
a push rod 9, the push rod 9 passing through the second end of the buffer cylinder 16 and being connected to the buffer piston 8; the push rod 9 is used for pulling the buffer piston 8 to move towards the second end of the buffer cylinder 16 in the middle pressure wave crest period of free exhaust and pushing the buffer piston 8 to move towards the first end of the buffer cylinder 16 in the end pressure wave trough period of forced exhaust.
In specific implementation, the control valve 7 is opened under the low-speed steady-state working condition of the engine; in the middle stage of free exhaust, the valve exhaust speed is high, the push rod 9 pulls the buffer piston 8 to move towards the second end of the buffer cylinder 16, the excessive pressure in the exhaust manifold 4 caused by high-speed exhaust is reduced, and in the final stage of forced exhaust, the exhaust speed is low, the buffer piston 8 moves towards the first end of the buffer cylinder 16, so that the pressure of the exhaust manifold 4 is improved, the pistons are cycled and reciprocated, the fluctuation amplitude of the pressure in the exhaust manifold 4 is reduced, the pumping loss of the exhaust of the cylinder 2 is reduced, the inlet pressure of the turbine 3 is relatively stable, and the efficiency of the turbine 3 is improved.
When the engine is in a high-speed working condition, the control valve 7 is closed, the buffer piston 8 is controlled to stop moving, the exhaust pipe system works in a conventional exhaust pipe system, at the moment, the actual effective flow area of the variable turbine 3 is larger, the reflection of pressure waves is weaker, the pressure fluctuation range in the exhaust pipe cannot be too high, and the exhaust pipe can maintain enough boost pressure due to the larger air flow flowing through the engine, so that the boost system has good transient performance.
In particular, the exhaust manifold 4 communicates with the corresponding cylinders 2 via a plurality of exhaust manifolds, respectively.
As a preferred form, it further comprises a clutch 10 and a transmission mechanism, a first end of which is in driving connection with the crankshaft 1 via the clutch 10, and a second end of which is connected with the push rod 9. Thus, under the high-speed working condition of the engine, the transmission between the transmission mechanism and the crankshaft 1 is conveniently cut off, and under the low-speed steady-state working condition of the engine, the power is conveniently transmitted to the push rod 9 from the crankshaft 1 through the transmission mechanism. Further, the transmission mechanism comprises a first belt pulley 11, a second belt pulley 12, a buffer crank 13 and a buffer connecting rod 14; the first belt pulley 11 is in transmission connection with the clutch 10, and the first belt pulley 11 is connected with the second belt pulley 12 through a belt 15; the first end of the buffer crank 13 is connected with the second belt wheel 12, the second end of the buffer crank 13 is hinged with the first end of the buffer connecting rod 14, and the second end of the buffer connecting rod 14 is hinged with one end of the push rod 9 located outside the buffer cylinder 16. In this way, the rotation of the crankshaft 1 can be converted into the reciprocating motion of the cushion piston 8. Further, the first pulley 11 and the second pulley 12 are toothed pulleys, and the belt 15 is a toothed belt. In this way, relative sliding between the belt 15 and the first pulley 11 or the second pulley 12 can be prevented, so that accuracy of movement can be ensured. Specifically, the transmission ratio between the first pulley 11 and the second pulley 12 is 4. In particular, one side of the second pulley 12 is rotatably mounted by a rotating shaft coaxially arranged therewith, and the other side is fixedly connected to one end of the buffer crank 13. In this way, interference between the rotating shaft and the buffer crank 13 during transmission can be prevented.
Preferably, the push rod 9 is slidably and sealingly connected to the buffer cylinder 16. Further, the buffer cylinder 16 is slidably and sealingly connected to the buffer piston 8. In this way, air leakage between the buffer cylinder 16 and the buffer piston 8 can be prevented, which is advantageous in reducing the pulse width.
When the engine is particularly used, under a low-speed steady-state working condition of the engine, the control valve 7 is opened, the clutch 10 is combined, the crankshaft 1 drives the first belt pulley 11 through the clutch 10, the first belt pulley 11 drives the second belt pulley 12 through the belt 15, the second belt pulley 12 drives the buffer crank 13 to rotate, the buffer piston 8 reciprocates in the buffer cylinder 16 under the drive of the buffer connecting rod 14, the valve exhaust speed is high in the middle free exhaust period, the buffer piston 8 moves towards the second end of the buffer cylinder 16, the pressure of the exhaust manifold 4 caused by high-speed exhaust is reduced, the valve exhaust speed is low in the end of forced exhaust, the buffer piston 8 moves towards the first end of the buffer cylinder 16, the pressure in the exhaust manifold 4 is improved, the buffer piston 8 circulates and reciprocates, the pressure fluctuation amplitude in the exhaust manifold 4 is reduced, the pumping loss of the exhaust of the cylinder 2 is reduced, the inlet pressure of the turbine 3 is relatively stable, and the efficiency of the turbine 3 is improved.
When the engine is in a high-speed working condition, the control valve 7 is closed, the clutch 10 is disconnected, the exhaust pipe system works in a conventional exhaust pipe system, at the moment, the actual effective flow area of the variable turbine 3 is larger, the reflection of pressure waves is weaker, the pressure fluctuation range in the exhaust manifold 4 cannot be too high, and the exhaust pipe can maintain enough boost pressure due to the larger air flow flowing through the engine, so that the boost system has good transient performance.
In particular, the diameter of the buffer piston 8 is 4-8 times, preferably 4 times, the diameter of the exhaust manifold 4, and the diameter of the exhaust manifold 4 is 1-2 times, preferably 2 times, the diameter of the bypass pipe 5. In this way, the pressure in the exhaust manifold 4 can be significantly changed when the cushion piston 8 moves.
In practice, the transmission of the first pulley 11 and the second pulley 12 is equal to the number of cylinders 2/2 of the engine, so that the number of cylinders/2 of the pressure pulse amplitude generated by the exhaust of all cylinders in one cycle of the four-stroke engine operation is suppressed.
In the specific implementation, during the working process of the engine, along with the interval of the exhaust stroke, the pressure in the exhaust manifold 4 is continuously changed, and the pressure peak period refers to the time period when the pressure in the exhaust manifold 4 is at the peak; the pressure trough period referred to in the present invention means a period in which the pressure in the exhaust manifold 4 is at the trough.
While the foregoing is directed to embodiments of the present invention, other and further embodiments of the invention may be devised without departing from the basic scope thereof, and the scope thereof is determined by the claims that follow.
Claims (5)
1. The utility model provides a piston pulse energy delayed release turbocharging device, includes bent axle (1), cylinder (2), turbine (3), exhaust manifold (4), bent axle (1) with the piston drive connection in cylinder (2), exhaust manifold (4) are used for communicating with cylinder (2) when exhausting, the waste gas import of turbine (3) with exhaust manifold (4) intercommunication, the waste gas export of turbine (3) is equipped with turbine back blast pipe (6);
characterized by further comprising:
a buffer cylinder (16), wherein a first end of the buffer cylinder (16) is communicated with the exhaust manifold (4), and a second end of the buffer cylinder (16) is communicated with the turbine rear exhaust pipe (6) through a bypass pipe (5);
a control valve (7), wherein the control valve (7) is arranged at the joint of the buffer cylinder (16) and the exhaust manifold (4);
-a buffer piston (8), the buffer piston (8) being slidably arranged within the buffer cylinder (16);
a push rod (9), the push rod (9) passing through the second end of the buffer cylinder (16) and being connected with the buffer piston (8); the push rod (9) is used for pulling the buffer piston (8) to move towards the second end of the buffer cylinder (16) in the middle pressure wave crest period of free exhaust and pushing the buffer piston (8) to move towards the first end of the buffer cylinder (16) in the tail pressure wave trough period of exhaust;
the device also comprises a clutch (10) and a transmission mechanism, wherein the first end of the transmission mechanism is in transmission connection with the crankshaft (1) through the clutch (10), and the second end of the transmission mechanism is connected with the push rod (9);
under the low-speed steady-state working condition of the engine, the control valve (7) is opened; in the middle stage of free exhaust, the exhaust speed of a valve is high, a push rod (9) pulls a buffer piston (8) to move towards the second end of a buffer cylinder (16), so that the excessive pressure in an exhaust manifold (4) caused by high-speed exhaust is reduced, in the end stage of forced exhaust, the exhaust speed is low, the buffer piston (8) moves towards the first end of the buffer cylinder (16), so that the pressure of the exhaust manifold (4) is improved, a control valve (7) is closed, the buffer piston (8) is controlled to stop moving under the high-speed working condition of an engine, and the exhaust manifold system works in a conventional exhaust pipe system;
the transmission mechanism comprises a first belt wheel (11), a second belt wheel (12), a buffer crank (13) and a buffer connecting rod (14);
the first belt wheel (11) is in transmission connection with the clutch (10), and the first belt wheel (11) is connected with the second belt wheel (12) through a belt (15); the first end of the buffer crank (13) is connected with the second belt wheel (12), the second end of the buffer crank (13) is hinged with the first end of the buffer connecting rod (14), and the second end of the buffer connecting rod (14) is hinged with one end of the push rod (9) located outside the buffer cylinder (16).
2. The piston pulse energy delayed release turbocharger as defined in claim 1, wherein said first pulley (11) and said second pulley (12) are toothed pulleys and said belt (15) is a toothed belt.
3. The piston pulse energy delayed release turbocharger according to claim 2, characterized in that the transmission ratio between the first pulley (11) and the second pulley (12) is half the number of cylinders to which the exhaust manifold is connected.
4. The piston pulse energy delayed release turbocharger according to claim 1, characterized in that the push rod (9) is slidably and sealingly connected to the buffer cylinder (16).
5. The piston pulse energy delayed release turbocharger according to claim 1, characterized in that the buffer cylinder (16) is slidably and sealingly connected to the buffer piston (8).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710969290.4A CN107701297B (en) | 2017-10-18 | 2017-10-18 | Piston type pulse energy delayed release turbocharging device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710969290.4A CN107701297B (en) | 2017-10-18 | 2017-10-18 | Piston type pulse energy delayed release turbocharging device |
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| Publication Number | Publication Date |
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| CN107701297A CN107701297A (en) | 2018-02-16 |
| CN107701297B true CN107701297B (en) | 2023-08-11 |
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| CN201710969290.4A Active CN107701297B (en) | 2017-10-18 | 2017-10-18 | Piston type pulse energy delayed release turbocharging device |
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