CN205277634U - Exhaust gas recirculation system for supercharged engine of formula of lighting - Google Patents
Exhaust gas recirculation system for supercharged engine of formula of lighting Download PDFInfo
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- CN205277634U CN205277634U CN201521134469.0U CN201521134469U CN205277634U CN 205277634 U CN205277634 U CN 205277634U CN 201521134469 U CN201521134469 U CN 201521134469U CN 205277634 U CN205277634 U CN 205277634U
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Abstract
The utility model provides an exhaust gas recirculation system for supercharged engine of formula of lighting, including the admission line, the air throttle, air intake manifold, the booster, exhaust duct, exhaust manifold, processing apparatus behind the waste gas, first intercooler, the bypass valve, a EGR valve, the first pipeline that has first port and second port, the second intercooler parallelly connected with the bypass valve, the 2nd EGR valve, there is the fourth port and with the second pipeline of the third port of first pipeline intercommunication and communicate first pipeline and the multi -ported valve of second pipeline, exhaust duct intercommunication behind first port and exhaust manifold and the waste gas between processing apparatus, admission line intercommunication between second port and air throttle and air intake manifold, the fourth port communicates with the admission line at the booster upper reaches, the control multi -ported valve makes the defeated waste gas of first pipeline, and it makes multi -ported valve and second port intercommunication to control the bypass valve, or it is defeated to air intake manifold through first port and fourth port with waste gas. This exhaust gas recirculation system has improved EGR rates, has improved the oil consumption.
Description
Technical field
The utility model relates to the gas recirculation system of a kind of engine, the engine with supercharger gas recirculation system of especially a kind of spark ignition type.
Background technology
Improving engine thermal efficiency, reducing oil consumption is the important topic that automotive industry faces. For petrol motor, comparing diesel engine, the major cause that petrol motor thermo-efficiency is lower comprises low geometrical compression ratio, high pumping loss and low gas mixture specific heat ratio etc. Wherein, the major cause that geometrical compression ratio is low is the knocking combustion of petrol motor at high loading. Gas recirculation system (EGR) refers to that the waste gas discharged by engine is after cooling, reenters the technology participating in burning in cylinder. The introducing of cooling EGR adds the specific heat capacity of end possible trouble gas mixture on the one hand so that the decrease in temperature of end gas mixture, thus pinking is suppressed. On the other hand, the rare gas element contained in EGR, can increase the degree of extinguishing reaction, thus extend the autoignition time of end gas mixture, reaches the effect suppressing pinking. Therefore, exterior cooling EGR is by improving geometrical compression ratio to the suppression of high loading pinking and strengthens the level of supercharging miniaturization, thus improves petrol motor thermo-efficiency. Meanwhile, in low-load region, due to the volume dilution effect of exterior cooling EGR, contribute to reducing the pumping loss of petrol motor, and the reduction of temperature of combustion is not only conducive to the increase of gas mixture specific heat ratio, is also conducive to the reduction of heat transfer loss. The advantage of these aspects makes exterior cooling EGR technology possess the potentiality improving high engine load and underload thermo-efficiency, thus reduces oil consumption.
But, the two kinds of exterior cooling egr systems built on supercharging gasoline engine at present, i.e. high pressure EGR and low pressure EGR system, all can not realize maximumization that oil consumption improves in supercharging gasoline engine whole service region. The waste gas that high pressure EGR generally gets exhaust manifold is incorporated into intake manifold, as shown in Figure 1. And low pressure EGR gets waste gas after petrol motor tail-gas after treatment apparatus, introduce waste gas in the rear end of air filter, as shown in Figure 2. In FIG, intake ducting is provided with air filter 100, compressor 101 and butterfly 102, gas exhaust duct is provided with turbine 104 and exhaust aftertreatment device 105, getting exhaust pipeline is connected between engine 103 and turbine 104, also it is connected between butterfly 102 and engine 103, gets and exhaust pipeline is provided with charge air cooler 106 and high pressure EGR valve 107. In fig. 2, intake ducting is provided with air filter 200, compressor 201 and butterfly 202, gas exhaust duct is provided with turbine 204 and exhaust aftertreatment device 205, getting exhaust pipeline is connected on the gas exhaust duct in exhaust aftertreatment device 205 downstream, also it is connected between air filter 200 and compressor 201, gets and exhaust pipeline is provided with charge air cooler 206 and low pressure EGR valve 207. The structures shape of these two kinds of egr systems its can only operate within the scope of certain engine behaviour, can not covering engine whole service operating mode effectively, so the oil consumption in engine whole service operating mode cannot be improved. Below by detail.
The pressure difference (i.e. the difference of EGR valve upstream pressure and downstream pressure) that the primary condition that can outside EGR run is EGR valve both sides will for be just worth, and pressure difference is more big, it is possible to the EGR of introducing is more many. At high-load region, the particularly big load region of low speed, the increasing degree of intake manifold pressure is much larger than the pressure increasing degree of exhaust manifold end. High pressure EGR valve downstream pressure will be caused like this to be greater than upstream pressure, and namely the pressure difference of EGR valve both sides is zero is even negative. Therefore, high pressure EGR cannot work at the knocking zone of the big load of low speed. And for low pressure EGR, owing to waste gas is introduced after air filter, namely EGR valve downstream pressure is normal atmosphere substantially, and the engine back pressure of EGR valve upstream increases along with engine load and increases. Namely the pressure difference of EGR valve both sides is just, and increases with the increase of load. Therefore, low pressure EGR can run at the high-load region comprising the big load regional extent of low speed. What is more important, the major obstacle that restriction petrol motor geometrical compression ratio improves is exactly the knocking combustion in the big load region of low speed. Low pressure EGR is owing to it is in the pinking restraining effect in the big load region of low speed so that improves geometrical compression ratio and becomes possibility. But it is to be noted, along with the further raising of petrol motor geometrical compression ratio and rate of supercharging, the maximum EGR rate that low pressure EGR system can realize at high-load region is also improved by further, and this causes current low pressure EGR system as shown in Figure 2 can not meet the requirement that high-load region improves EGR rate completely. In low-load region, intake manifold pressure is equal to or less than normal atmosphere, and therefore, the pressure difference of high pressure EGR valve both sides is bigger, it is possible to realize bigger EGR rate. And the pressure reduction of current low pressure EGR valve both sides depends primarily on engine exhaust back pressure, under low-load region, exhaust back pressure is lower, and therefore, low pressure EGR system is difficult to realize bigger EGR rate at underload, and fuel-economizing potentiality will lower than high pressure egr system. In sum, high pressure EGR and low pressure EGR respectively have relative merits, improve to all realize good oil consumption in engine whole service region, just existing high pressure and low pressure EGR system must be improved, enable outside EGR cover whole engine speed/load region, and manage to improve EGR rate.
Practical novel content
The purpose of this utility model is to provide the engine with supercharger gas recirculation system of a kind of spark ignition type, to solve the existing egr system problem that oil consumption is relatively big under engine whole service operating mode, EGR rate is lower.
In order to achieve the above object, the utility model provides the engine with supercharger gas recirculation system of a kind of spark ignition type, comprising:
Air inlet module, the butterfly comprise intake ducting, being arranged on intake ducting and the intake manifold being connected with intake ducting and engine respectively;
Supercharging blower, is arranged on described intake ducting, and is positioned at the upstream of described butterfly;
Exhaust module, comprises gas exhaust duct, the exhaust manifold being connected respectively and the exhaust aftertreatment device being arranged on gas exhaust duct with engine and gas exhaust duct;
First gets waste gas module, comprise the first charge air cooler, by-pass valve, the first EGR valve and there is the first pipeline of the first port and Two-port netwerk, described first port is connected with the gas exhaust duct between described exhaust manifold and exhaust aftertreatment device, described Two-port netwerk is connected with the intake ducting between described butterfly and intake manifold, described first charge air cooler, by-pass valve and the first EGR valve are separately positioned on the first pipeline, and described first charge air cooler and by-pass valve are arranged in parallel;
2nd gets waste gas module, comprise the 2nd charge air cooler, the 2nd EGR valve and there is the 3rd port and the second pipe of the 4th port, described 3rd port and the first pipeline communication, described 4th port is connected with the intake ducting of supercharging blower upstream, and described 2nd charge air cooler and the 2nd EGR valve are separately positioned on second pipe;
Multiport valve, the connectivity part being arranged on described first pipeline and second pipe, and there is the five-port being connected with the first port, the 6th port that is connected with Two-port netwerk through the first charge air cooler or by-pass valve and the first EGR valve and the 7th port being connected with the 3rd port;
Wherein, make to adopt first to get waste gas module and carried to intake manifold place through the first pipeline by waste gas by controlling described multiport valve, and by controlling described by-pass valve, the 6th port of described multiport valve is connected with described Two-port netwerk through the first charge air cooler or by-pass valve and the first EGR valve, or adopt the described 2nd to get waste gas module to be carried to intake manifold place through the first port, the 3rd port and the 4th port successively by waste gas.
Further, under engine low load operating mode, by control described multiport valve make adopt first get waste gas module by waste gas through the first pipeline to intake manifold place conveying, by controlling described by-pass valve, the 6th port of described multiport valve is connected with described Two-port netwerk through by-pass valve and the first EGR valve.
Further, the load that the running on the lower load of engine is corresponding is: 0��P1*Lm, and wherein, P1:20%��40%, Lm is the maximum load of engine.
Further, within the engine under load condition, by control described multiport valve make adopt first get waste gas module by waste gas through the first pipeline to intake manifold place conveying, by controlling described by-pass valve, the 6th port of described multiport valve is connected with described Two-port netwerk through the first charge air cooler and the first EGR valve.
Further, the load that the middle load condition of engine is corresponding is: P1*Lm��P2*Lm, and wherein, P1:20%��40%, P2:30%��60%, P2 is greater than P1, and Lm is the maximum load of engine.
Further, under high engine load operating mode, make to adopt the 2nd to get waste gas module and carried to intake manifold place through the first port, the 3rd port and the 4th port successively by waste gas by controlling described multiport valve.
Further, the load that the high loading operating mode of engine is corresponding is: P2*Lm��Lm, and wherein, P2:30%��60%, Lm is the maximum load of engine.
Further, described first EGR valve is high pressure EGR valve, and the pressure reduction scope at described high pressure EGR valve two ends is: 0��H1, wherein, and H1:20��150 kPa.
Further, described 2nd EGR valve is low pressure EGR valve, and the pressure reduction scope at described low pressure EGR valve two ends is: 0��L1, wherein, and L1:10��100 kPa.
Further, described air inlet module also comprises air filter, 3rd charge air cooler and the inlet manifold being connected with intake ducting, described air filter is arranged on intake ducting, and it is positioned at the upstream of described supercharging blower, described 3rd charge air cooler is arranged on intake ducting, and it is positioned at the upstream of described butterfly, described inlet manifold is fixed in intake manifold, and the Two-port netwerk with described first pipeline is connected, described exhaust module also comprises the exhaust-gas receiver being connected with gas exhaust duct, described exhaust-gas receiver is fixed on exhaust manifold, and the first port with described first pipeline is connected, described engine is petrol motor or diesel engine, described exhaust aftertreatment device is ternary catalyzing unit or ternary catalyzing unit and grain catcher, described 2nd gets waste gas module also comprises particulate filter, described particulate filter is arranged on second pipe, described multiport valve is T-valve, described first EGR valve and the 2nd EGR valve are driven by motor respectively, described multiport valve is automatically controlled multiport valve, described by-pass valve is automatically controlled by-pass valve, described first charge air cooler and by-pass valve are arranged on the upstream of the first EGR valve simultaneously, it is arranged on the downstream of the first EGR valve simultaneously or it is arranged on the upstream and downstream of the first EGR valve respectively simultaneously.
Further, described engine is turbosupercharged engine, mechanically-sapercharged engine or two engine with supercharger, and described engine is petrol motor, natural gas engine or ethanol engine.
Further, described engine with supercharger is turbosupercharged engine, described supercharging blower comprises compressor and turbine, and described compressor is arranged on the described 4th intake ducting between port and butterfly, and described turbine is arranged on the gas exhaust duct in described first port downstream.
The utility model additionally provides the using method of the engine with supercharger gas recirculation system of a kind of spark ignition type, it is applied on the engine with supercharger gas recirculation system of described spark ignition type, this using method comprises: make to adopt first to get waste gas module and carried to intake manifold place through the first pipeline by waste gas by controlling described multiport valve, and by controlling described by-pass valve, the 6th port of described multiport valve is connected with described Two-port netwerk through the first charge air cooler or by-pass valve and the first EGR valve, or adopt the described 2nd to get waste gas module by waste gas successively through the first port, 3rd port and the 4th port are carried to intake manifold place.
Further, when engine is running on the lower load, by control described multiport valve make adopt first get waste gas module by waste gas through the first pipeline to intake manifold place conveying, open described by-pass valve and the 6th port of described multiport valve be connected with described Two-port netwerk through by-pass valve and the first EGR valve;
When engine is middle load condition, by control described multiport valve make adopt first get waste gas module by waste gas through the first pipeline to intake manifold place conveying, close described by-pass valve and the 6th port of described multiport valve be connected with described Two-port netwerk through the first charge air cooler and the first EGR valve.
When engine is high loading operating mode, make to adopt the 2nd to get waste gas module and carried to intake manifold place through the first port, the 3rd port and the 4th port successively by waste gas by controlling described multiport valve.
The utility model provides the engine with supercharger gas recirculation system of a kind of spark ignition type, this gas recirculation system comprises two-way EGR circuit, high hydraulic circuit is provided with charge air cooler and by-pass valve, waste gas is made to keep temperature or cool by controlling the break-make of by-pass valve, engine low load and the oil consumption level of middle load condition scope can be reduced, low hydraulic circuit arranges charge air cooler, and low hydraulic circuit directly gets waste gas from exhaust manifold, the pinking of high engine load is inhibited, improve the oil consumption simultaneously also reducing high engine load of geometrical compression ratio, finally achieve the object improving EGR rate within the scope of engine full working scope He improving oil consumption.
Accompanying drawing explanation
Fig. 1 is the structural representation of prior art mesohigh egr system;
Fig. 2 is the structural representation of low pressure EGR system in prior art;
The structural representation of the engine with supercharger gas recirculation system of the spark ignition type that Fig. 3 provides for the utility model embodiment.
In figure, 100: air filter, 101: compressor, 102: butterfly, 103: engine, 104: turbine, 105: exhaust aftertreatment device, 106: charge air cooler, 107: high pressure EGR valve, 200: air filter, 201: compressor, 202: butterfly, 203: engine, 204: turbine, 205: exhaust aftertreatment device, 206: charge air cooler, 207: low pressure EGR valve, 1: air filter, 2: intake ducting, 3: supercharging blower, 31: compressor, 32: turbine, 4: the three charge air coolers, 5: butterfly, 6: intake manifold, 7: engine, 8: exhaust manifold, 9: gas exhaust duct, 10: exhaust aftertreatment device, 11: the first pipelines, 111: the first ports, 112: the Two-port netwerk, 12: multiport valve, 121: the five-port, 122: the six ports, 123: the seven ports, 13: the first charge air coolers, 14: by-pass valve, 15: the first EGR valve, 16: second pipe, 161: the three ports, 162: the four ports, 17: the two charge air coolers, 18: the two EGR valve, 19: particulate filter.
Embodiment
Below in conjunction with schematic diagram, embodiment of the present utility model is described in more detail. Will be clearer according to following description and claim book, advantage of the present utility model and feature. It should be noted that, accompanying drawing all adopts the form simplified very much and all uses non-ratio accurately, only in order to object convenient, distinct ground aid illustration the utility model embodiment.
As shown in Figure 3, present embodiments provide the engine with supercharger gas recirculation system of a kind of spark ignition type, comprising:
Air inlet module, the butterfly 5 comprise intake ducting 2, being arranged on intake ducting 2 and the intake manifold 6 being connected with intake ducting 2 and engine 7 respectively;
Supercharging blower 3, is arranged on described intake ducting 2, and is positioned at the upstream of described butterfly 5;
Exhaust module, comprises gas exhaust duct 9, the exhaust manifold 8 being connected respectively and the exhaust aftertreatment device 10 being arranged on gas exhaust duct 9 with engine 7 and gas exhaust duct 9;
First gets waste gas module, comprise the first charge air cooler 13, by-pass valve 14, first EGR valve 15 and there is the first pipeline 11 of the first port 111 and Two-port netwerk 112, described first port 111 is connected with the gas exhaust duct 9 between described exhaust manifold 8 and exhaust aftertreatment device 10, intake ducting 2 between described Two-port netwerk 112 with described butterfly 5 and intake manifold 6 is connected, described first charge air cooler 13, by-pass valve 14 and the first EGR valve 15 are separately positioned on the first pipeline 11, and described first charge air cooler 13 and by-pass valve 14 are arranged in parallel;
2nd gets waste gas module, comprise the 2nd charge air cooler 17, the 2nd EGR valve 18 and there is the 3rd port 161 and the second pipe 16 of the 4th port 162, described 3rd port 161 is connected with the first pipeline 11, described 4th port 162 is connected with the intake ducting 2 of supercharging blower 3 upstream, and described 2nd charge air cooler 17 and the 2nd EGR valve 18 are separately positioned on second pipe 16;
Multiport valve 12, the connectivity part being arranged on described first pipeline 11 and second pipe 16, and there is the five-port 121 being connected with the first port 111, the 6th port 122 that is connected with Two-port netwerk 112 through the first charge air cooler 13 or by-pass valve 14 and the first EGR valve 15 and the 7th port 123 being connected with the 3rd port 161;
Wherein, make to adopt first to get waste gas module and carried to intake manifold 6 place through the first pipeline 11 by waste gas by controlling described multiport valve 12, and by controlling described by-pass valve 14, the 6th port of described multiport valve 12 is connected with described Two-port netwerk 112 through the first charge air cooler 13 or by-pass valve 14 and the first EGR valve 15, or adopt the described 2nd to get waste gas module to be carried to intake manifold 6 place through the first port 111, the 3rd port 161 and the 4th port 162 successively by waste gas.
Under engine low load operating mode, by control described multiport valve 12 make adopt first get waste gas module by waste gas through the first pipeline 11 to intake manifold 6 place conveying, by controlling described by-pass valve 14, the 6th port 122 of described multiport valve 12 is connected with described Two-port netwerk 112 through by-pass valve 14 and the first EGR valve 15. Also it is exactly that waste gas, without the cooling of the first charge air cooler 13, keeps original high temperature to enter engine 7 through the first EGR valve 15 of high pressure. Now, not only achieve maximumization of the first EGR valve 15 both sides pressure reduction of high pressure, and waste gas is without cooling, contributes to the combustion stability that engine 7 keeps good under high EGR rate, thus reach maximized oil consumption and improve.
Within the engine under load condition, by control described multiport valve 12 make adopt first get waste gas module by waste gas through the first pipeline 11 to intake manifold 6 place conveying, by controlling described by-pass valve 14, the 6th port 122 of described multiport valve 12 is connected with described Two-port netwerk 112 through the first charge air cooler 13 and the first EGR valve 15. Also it is exactly that waste gas flows through the first EGR valve 15 of high pressure after the cooling of the first charge air cooler 13, and finally enters engine 7. Under middle load condition, the exhaust temperature of engine wants high relative to running on the lower load, and the waste gas of high temperature enters engine and the temperature of gas mixture can be made to raise, thus increases the weight of the tendency of engine generation pinking so that engine thermal efficiency declines, and oil consumption rises. And EGR exhaust is after the cooling of the first charge air cooler 13, reducing temperature, reduce the tendency that engine knock increases the weight of, the engine consumption reaching best improves.
Under high engine load operating mode, make to adopt the 2nd to get waste gas module and carried to intake manifold 6 place through the first port 111, the 3rd port 161 and the 4th port 162 successively by waste gas by controlling described multiport valve 12. Also it is exactly close high pressure EGR circuit so that low pressure EGR loop works. Under high engine load operating mode, the major technical challenge that engine faces is knocking combustion. Pinking directly results in engine thermal efficiency decline, and oil consumption rises. Exterior cooling EGR is due to its advantage in pinking suppression, and engine knock burning is inhibited, thus reaches the object improving oil consumption. In the present embodiment, the waste gas in low pressure EGR loop is not get after exhaust aftertreatment device 10 common at present, but get (in the present embodiment from the exhaust manifold 8 the same with high pressure EGR circuit, get from exhaust-gas receiver), the pressure of the 2nd EGR valve upstream of low pressure is increased, thus realize bigger low pressure EGR flow, to reach pinking suppression and the object of fuel economy improvement further.
For different engines, the running on the lower load of each engine usually can not be identical. For middle load condition and high loading operating mode, being also like this, those skilled in the art need the type according to engine to determine the concrete scope of its running on the lower load, middle load condition and high loading operating mode.
As a non-limiting embodiment, the load that the running on the lower load of engine is corresponding is: 0��P1*Lm, the load that the middle load condition of engine is corresponding is: P1*Lm��P2*Lm, the load that the high loading operating mode of engine is corresponding is: P2*Lm��Lm, wherein, P1:20%��40%, P2:30%��60%, P2 is greater than P1, and Lm is the maximum load of engine.
Please continue to refer to Fig. 1, as a unrestricted example, in the present embodiment, described first EGR valve 15 is high pressure EGR valve, and the pressure reduction scope at described high pressure EGR valve two ends is: 0��H1, wherein, and H1:20��150 kPa; Described 2nd EGR valve 18 is low pressure EGR valve, and the pressure reduction scope at described low pressure EGR valve two ends is: 0��L1, wherein, and L1:10��100 kPa.
Further, described air inlet module also comprises air filter 1, 3rd charge air cooler 4 and the inlet manifold's (not marking in figure) being connected with intake ducting 2, described air filter 1 is arranged on intake ducting 2, and it is positioned at the upstream of described supercharging blower 3, described 3rd charge air cooler 4 is arranged on intake ducting 2, and it is positioned at the upstream of described butterfly 5, described inlet manifold is fixed in intake manifold 6, and the Two-port netwerk 112 with described first pipeline 11 is connected, described exhaust module also comprises the exhaust-gas receiver (not marking in figure) being connected with gas exhaust duct 9, described exhaust-gas receiver is fixed on exhaust manifold 8, and the first port 111 with described first pipeline 11 is connected.
Described (spark ignition type) engine 7 can be petrol motor, natural gas engine or ethanol engine, and in the present embodiment, it is petrol motor. Described exhaust aftertreatment device 10 is ternary catalyzing unit or ternary catalyzing unit and grain catcher, described 2nd gets waste gas module also comprises particulate filter 19, described particulate filter 19 is arranged on second pipe 16, the effect of particulate filter 19 is filtered out by the macrobead thing contained in waste gas, affect the supercharging blower life-span to avoid the compressor chamber entering turbo-supercharger, cause turbocharger impairment.
Multiport valve 12 has five-port 121, the 6th port 122 and the 7th port 123, therefore this multiport valve 12 is at least T-valve. For this multiport valve 12 as four-way valve, the quantity of one of the five-port 121 of four-way valve, the 6th port 122 and the 7th port 123 is two, such as, the quantity of five-port 121 is two, then arrange two first pipelines 11 between exhaust-gas receiver and two five-port 121. In the present embodiment, described multiport valve 12 is preferably T-valve.
Described first EGR valve 15, the 2nd EGR valve 18, multiport valve 12 and by-pass valve 14 can adopt multiple type of drive respectively. Such as, described first EGR valve 15 is driven by motor or solenoid-driven, and described 2nd EGR valve 18 is driven by motor or solenoid-driven, and described multiport valve 12 adopts hydraulic drive or electric drive, and described by-pass valve 14 adopts hydraulic drive or electric drive, but is not limited to this. In the present embodiment, described first EGR valve 15 and the 2nd EGR valve 18 are driven by motor respectively, the flow of waste gas realizes continuously adjustabe by motor-driven first EGR valve 15, also realize continuously adjustabe by motor-driven 2nd EGR valve 18, described multiport valve 12 is automatically controlled multiport valve, and described by-pass valve 14 is automatically controlled by-pass valve. In addition, described first charge air cooler 13 and by-pass valve 14 are arranged on the upstream of the first EGR valve 15, the downstream being simultaneously arranged on the first EGR valve 15 simultaneously or are arranged on the upstream and downstream (namely the upstream of the first EGR valve has the first charge air cooler and by-pass valve, and downstream also has the first charge air cooler and by-pass valve) of the first EGR valve 15 respectively simultaneously.
Described (supercharging) engine 7 is turbosupercharged engine, mechanically-sapercharged engine or two engine with supercharger. In the present embodiment, described engine with supercharger is turbosupercharged engine, described supercharging blower 3 comprises compressor 31 and turbine 32, described compressor 31 is arranged on the intake ducting 2 between described 4th port 162 and butterfly 5, described turbine 32 is arranged on the gas exhaust duct 9 in described first port 111 downstream, described 3rd charge air cooler 4 is arranged on the intake ducting 2 between compressor 31 and butterfly 5, and the 4th port 162 of described second pipe 16 is connected on the intake ducting 2 between air filter 1 and compressor 31.
, it provides the egr system of a kind of double loop, to sum up, in the present embodiment this system can under engine full working scope (i.e. all rotating speeds and load within the scope of) realize the EGR rate expected. Existing whether high pressure EGR or low pressure EGR system, all can only work in limited motor speed load region, and the egr system that the utility model proposes, contain two-way egr system, can according to the combustion needs of engine, switching between this two covers EGR circuit, such that it is able to all realize the EGR rate expected under all motor speed and load condition. In the present embodiment, high pressure EGR circuit devises the bypass function of waste gas charge air cooler, such that it is able to according to the needs of engine combustion, and cold two kinds of operating mode in selecting cold in waste gas or waste gas not. In addition, in the present embodiment, the waste gas in low pressure EGR loop is not get after exhaust aftertreatment device common at present, but get from the exhaust-gas receiver the same with high pressure EGR circuit, the pressure of low pressure EGR valve upstream is increased, thus realize bigger low pressure EGR flow, meet the demand of the bigger EGR rate that engine proposes at high-load region, to reach pinking suppression and the object of fuel economy improvement further.
The present embodiment additionally provides the using method of the engine with supercharger gas recirculation system of a kind of spark ignition type, it is applied on the engine with supercharger gas recirculation system of described spark ignition type, this using method comprises: make to adopt first to get waste gas module and carried to intake manifold 6 place through the first pipeline 11 by waste gas by controlling described multiport valve 12, and by controlling described by-pass valve 14, the 6th port 122 of described multiport valve 12 is connected with described Two-port netwerk 112 through the first charge air cooler 13 or by-pass valve 14 and the first EGR valve 15, or adopt the described 2nd to get waste gas module by waste gas successively through the first port 111, 3rd port 161 and the 4th port 162 are carried to intake manifold 6 place.
When engine is running on the lower load, by control described multiport valve 12 make adopt first get waste gas module by waste gas through the first pipeline 11 to intake manifold 6 place conveying, open described by-pass valve 14 and the 6th port 122 of described multiport valve 12 be connected with described Two-port netwerk 112 through by-pass valve 14 and the first EGR valve 15;
When engine is middle load condition, by control described multiport valve 12 make adopt first get waste gas module by waste gas through the first pipeline 11 to intake manifold 6 place conveying, close described by-pass valve 14 and the 6th port 122 of described multiport valve 12 be connected with described Two-port netwerk 112 through the first charge air cooler 13 and the first EGR valve 15.
When engine is high loading operating mode, make to adopt the 2nd to get waste gas module and carried to intake manifold 6 place through the first port 112, the 3rd port 161 and the 4th port 162 successively by waste gas by controlling described multiport valve 12.
The utility model provides the engine with supercharger gas recirculation system of a kind of spark ignition type, this gas recirculation system comprises two-way EGR circuit, high hydraulic circuit is provided with charge air cooler and by-pass valve, waste gas is made to keep temperature or cool by controlling the break-make of by-pass valve, engine low load and the oil consumption level of middle load condition scope can be reduced, low hydraulic circuit arranges charge air cooler, and low hydraulic circuit directly gets waste gas from exhaust manifold, the pinking of high engine load is inhibited, improve the oil consumption simultaneously also reducing high engine load of geometrical compression ratio, finally achieve the object improving EGR rate within the scope of engine full working scope He improving oil consumption.
Above are only preferred embodiment of the present utility model, the utility model is not played any restriction. Any person of ordinary skill in the field; in the scope not departing from the technical solution of the utility model; the technical scheme and the technology contents that disclose the utility model make the variations such as any type of equivalent replacement or amendment; all belong to the content not departing from the technical solution of the utility model, still belong within protection domain of the present utility model.
Claims (12)
1. the engine with supercharger gas recirculation system of a spark ignition type, it is characterised in that, comprising:
Air inlet module, the butterfly comprise intake ducting, being arranged on intake ducting and the intake manifold being connected with intake ducting and engine respectively;
Supercharging blower, is arranged on described intake ducting, and is positioned at the upstream of described butterfly;
Exhaust module, comprises gas exhaust duct, the exhaust manifold being connected respectively and the exhaust aftertreatment device being arranged on gas exhaust duct with engine and gas exhaust duct;
First gets waste gas module, comprise the first charge air cooler, by-pass valve, the first EGR valve and there is the first pipeline of the first port and Two-port netwerk, described first port is connected with the gas exhaust duct between described exhaust manifold and exhaust aftertreatment device, described Two-port netwerk is connected with the intake ducting between described butterfly and intake manifold, described first charge air cooler, by-pass valve and the first EGR valve are separately positioned on the first pipeline, and described first charge air cooler and by-pass valve are arranged in parallel;
2nd gets waste gas module, comprise the 2nd charge air cooler, the 2nd EGR valve and there is the 3rd port and the second pipe of the 4th port, described 3rd port and the first pipeline communication, described 4th port is connected with the intake ducting of supercharging blower upstream, and described 2nd charge air cooler and the 2nd EGR valve are separately positioned on second pipe;
Multiport valve, the connectivity part being arranged on described first pipeline and second pipe, and there is the five-port being connected with the first port, the 6th port that is connected with Two-port netwerk through the first charge air cooler or by-pass valve and the first EGR valve and the 7th port being connected with the 3rd port;
Wherein, make to adopt first to get waste gas module and carried to intake manifold place through the first pipeline by waste gas by controlling described multiport valve, and by controlling described by-pass valve, the 6th port of described multiport valve is connected with described Two-port netwerk through the first charge air cooler or by-pass valve and the first EGR valve, or adopt the described 2nd to get waste gas module to be carried to intake manifold place through the first port, the 3rd port and the 4th port successively by waste gas.
2. the engine with supercharger gas recirculation system of spark ignition type as claimed in claim 1, it is characterized in that, under engine low load operating mode, by control described multiport valve make adopt first get waste gas module by waste gas through the first pipeline to intake manifold place conveying, by controlling described by-pass valve, the 6th port of described multiport valve is connected with described Two-port netwerk through by-pass valve and the first EGR valve.
3. the engine with supercharger gas recirculation system of spark ignition type as claimed in claim 2, it is characterised in that, the load that the running on the lower load of engine is corresponding is: 0��P1*Lm, and wherein, P1:20%��40%, Lm is the maximum load of engine.
4. the engine with supercharger gas recirculation system of spark ignition type as claimed in claim 1, it is characterized in that, within the engine under load condition, by control described multiport valve make adopt first get waste gas module by waste gas through the first pipeline to intake manifold place conveying, by controlling described by-pass valve, the 6th port of described multiport valve is connected with described Two-port netwerk through the first charge air cooler and the first EGR valve.
5. the engine with supercharger gas recirculation system of spark ignition type as claimed in claim 4, it is characterised in that, the load that the middle load condition of engine is corresponding is: P1*Lm��P2*Lm, wherein, P1:20%��40%, P2:30%��60%, P2 is greater than P1, and Lm is the maximum load of engine.
6. the engine with supercharger gas recirculation system of spark ignition type as claimed in claim 1, it is characterized in that, under high engine load operating mode, make to adopt the 2nd to get waste gas module and carried to intake manifold place through the first port, the 3rd port and the 4th port successively by waste gas by controlling described multiport valve.
7. the engine with supercharger gas recirculation system of spark ignition type as claimed in claim 6, it is characterised in that, the load that the high loading operating mode of engine is corresponding is: P2*Lm��Lm, and wherein, P2:30%��60%, Lm is the maximum load of engine.
8. the engine with supercharger gas recirculation system of spark ignition type as claimed in claim 1, it is characterised in that, described first EGR valve is high pressure EGR valve, and the pressure reduction scope at described high pressure EGR valve two ends is: 0��H1, wherein, H1:20��150 kPa.
9. the engine with supercharger gas recirculation system of spark ignition type as claimed in claim 1, it is characterised in that, described 2nd EGR valve is low pressure EGR valve, and the pressure reduction scope at described low pressure EGR valve two ends is: 0��L1, wherein, L1:10��100 kPa.
10. the engine with supercharger gas recirculation system of spark ignition type as claimed in claim 1, it is characterized in that, described air inlet module also comprises air filter, 3rd charge air cooler and the inlet manifold being connected with intake ducting, described air filter is arranged on intake ducting, and it is positioned at the upstream of described supercharging blower, described 3rd charge air cooler is arranged on intake ducting, and it is positioned at the upstream of described butterfly, described inlet manifold is fixed in intake manifold, and the Two-port netwerk with described first pipeline is connected, described exhaust module also comprises the exhaust-gas receiver being connected with gas exhaust duct, described exhaust-gas receiver is fixed on exhaust manifold, and the first port with described first pipeline is connected, described engine is petrol motor or diesel engine, described exhaust aftertreatment device is ternary catalyzing unit or ternary catalyzing unit and grain catcher, described 2nd gets waste gas module also comprises particulate filter, described particulate filter is arranged on second pipe, described multiport valve is T-valve, described first EGR valve and the 2nd EGR valve are driven by motor respectively, described multiport valve is automatically controlled multiport valve, described by-pass valve is automatically controlled by-pass valve, described first charge air cooler and by-pass valve are arranged on the upstream of the first EGR valve simultaneously, it is arranged on the downstream of the first EGR valve simultaneously or it is arranged on the upstream and downstream of the first EGR valve respectively simultaneously.
The engine with supercharger gas recirculation system of 11. spark ignition types as claimed in claim 1, it is characterized in that, described engine is turbosupercharged engine, mechanically-sapercharged engine or two engine with supercharger, and described engine is petrol motor, natural gas engine or ethanol engine.
The engine with supercharger gas recirculation system of 12. spark ignition types as claimed in claim 11, it is characterized in that, described engine with supercharger is turbosupercharged engine, described supercharging blower comprises compressor and turbine, described compressor is arranged on the described 4th intake ducting between port and butterfly, and described turbine is arranged on the gas exhaust duct in described first port downstream.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201521134469.0U CN205277634U (en) | 2015-12-30 | 2015-12-30 | Exhaust gas recirculation system for supercharged engine of formula of lighting |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201521134469.0U CN205277634U (en) | 2015-12-30 | 2015-12-30 | Exhaust gas recirculation system for supercharged engine of formula of lighting |
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| Publication Number | Publication Date |
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| CN205277634U true CN205277634U (en) | 2016-06-01 |
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| CN201521134469.0U Withdrawn - After Issue CN205277634U (en) | 2015-12-30 | 2015-12-30 | Exhaust gas recirculation system for supercharged engine of formula of lighting |
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| CN (1) | CN205277634U (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105508088A (en) * | 2015-12-30 | 2016-04-20 | 联合汽车电子有限公司 | Waste gas recirculation system for spark ignition type supercharged engine and use method of waste gas recirculation system |
| CN106523201A (en) * | 2016-12-28 | 2017-03-22 | 无锡隆盛科技股份有限公司 | Multi-way EGR valve controller |
| CN107489521A (en) * | 2016-08-25 | 2017-12-19 | 宝沃汽车（中国）有限公司 | The control method of engine, the cooling system of engine and cooling system |
| CN111894765A (en) * | 2019-05-06 | 2020-11-06 | 广州汽车集团股份有限公司 | Exhaust gas recirculation system |
| CN112555079A (en) * | 2020-12-02 | 2021-03-26 | 长安大学 | Methanol fuel engine and starting control method thereof |
| CN112799371A (en) * | 2019-11-13 | 2021-05-14 | 北京福田康明斯发动机有限公司 | Control system and control method of engine particle number emission measuring device |
| CN117418969A (en) * | 2023-12-18 | 2024-01-19 | 潍柴动力股份有限公司 | EGR system and control method thereof |
-
2015
- 2015-12-30 CN CN201521134469.0U patent/CN205277634U/en not_active Withdrawn - After Issue
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105508088A (en) * | 2015-12-30 | 2016-04-20 | 联合汽车电子有限公司 | Waste gas recirculation system for spark ignition type supercharged engine and use method of waste gas recirculation system |
| CN107489521A (en) * | 2016-08-25 | 2017-12-19 | 宝沃汽车（中国）有限公司 | The control method of engine, the cooling system of engine and cooling system |
| CN106523201A (en) * | 2016-12-28 | 2017-03-22 | 无锡隆盛科技股份有限公司 | Multi-way EGR valve controller |
| CN111894765A (en) * | 2019-05-06 | 2020-11-06 | 广州汽车集团股份有限公司 | Exhaust gas recirculation system |
| CN112799371A (en) * | 2019-11-13 | 2021-05-14 | 北京福田康明斯发动机有限公司 | Control system and control method of engine particle number emission measuring device |
| CN112799371B (en) * | 2019-11-13 | 2022-05-13 | 北京福田康明斯发动机有限公司 | Control system and control method of engine particle number emission measuring device |
| CN112555079A (en) * | 2020-12-02 | 2021-03-26 | 长安大学 | Methanol fuel engine and starting control method thereof |
| CN112555079B (en) * | 2020-12-02 | 2022-11-25 | 长安大学 | Methanol fuel engine and starting control method thereof |
| CN117418969A (en) * | 2023-12-18 | 2024-01-19 | 潍柴动力股份有限公司 | EGR system and control method thereof |
| CN117418969B (en) * | 2023-12-18 | 2024-03-19 | 潍柴动力股份有限公司 | EGR system and control method thereof |
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