CN104948295A - Waste gas bypass valve of turbocharger - Google Patents
Waste gas bypass valve of turbocharger Download PDFInfo
- Publication number
- CN104948295A CN104948295A CN201510270887.0A CN201510270887A CN104948295A CN 104948295 A CN104948295 A CN 104948295A CN 201510270887 A CN201510270887 A CN 201510270887A CN 104948295 A CN104948295 A CN 104948295A
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- valve
- exhaust gas
- flow channel
- bypass flow
- opening portion
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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Abstract
The invention discloses a waste gas bypass valve of a turbocharger. The waste gas bypass valve is provided with a bypass flow channel and a valve element, a gas inlet and a gas outlet of a turbine are communicated through the bypass flow channel, and the valve element is used for opening or closing the opening part of the bypass flow channel. The valve element comprises a valve rod part and a valve plate part connected to the valve rod part, the valve rod part can axially move so that the valve plate part can be driven to horizontally move along the end face of the opening part of the bypass flow channel, and the end face of the opening part is opened or closed through the valve plate part. The waste gas bypass valve can improve control precision of an engine under various load work conditions, and enhance sealing performance of the waste gas bypass valve of the engine under a high load.
Description
Technical field
The present invention relates to engine turbine pressurization system, be specially a kind of exhaust gas by-pass valve for turbosupercharger.
Background technique
The fundamental function of pressurized machine exhaust gas by-pass valve regulates the bypass exhaust flow of charger turbine, thus the control realized pressurized machine and even motor complete machine MAF and intake and exhaust pressure and adjustment, ensure engine health stable operation; Due to the acting working medium that waste gas is motor, therefore exhaust gas by-pass valve is while adjustment waste gas, also comprises and regulates engine breathing pressure to keep fuel economy as well as possible, the abnormal sound noise avoiding waste gas to act on generation on component making us uncomfortable.
See Fig. 1, current exhaust gas turbocharge internal combustion engine, comprises engine body 1, gas compressor 2, exhaust gas by-pass valve 3, turbo machine 4, catalyst converter 5.Wherein, turbo machine 4 connecting engine vent systems, absorbs high-temp waste gas energy, and the gas compressor 2 promoting coaxial connection rotates and compresses fresh air and enters engine body 1.For the specific target operation load of motor, the exhaust gas flow by turbo machine 4 is regulated by exhaust gas by-pass valve 3, to regulate the working power of turbo machine 4, and then regulate the working power of gas compressor 2, thus regulate pressurized air boost pressure and mass flow rate, finally realize engine air system to regulate, support that engine workload regulates, export required torque power.
See Fig. 2, existing exhaust gas by-pass valve 3, comprises positive pressure pressure final controlling element 33, final controlling element pedestal 34, final controlling element push rod 33a, rocking arm 35, cover plate valve valve gap 32, bypass flow channel 31.Under default setting, the pilot pressure passing into positive pressure pressure final controlling element 33 is barometric pressure, and cover plate valve valve gap 32 closes bypass valve runner under its preload pressure effect, and therefore the default setting of valve is normal closing.When needs regulate engine workload, the pilot pressure of input positive pressure pressure final controlling element 33 raises, promote final controlling element push rod 33a, and then promote rocking arm 35, rotatable cover plate valve valve gap 32, open exhaust gas bypass runner 31, be reduced by the exhaust gas flow of turbo machine 4, regulate turbine loads, and then regulate the gas compressor load be coaxially connected with turbo machine, and then regulate the compressed air require of gas compressor 2, thus the auxiliary regulatory function realizing engine air system.
There is following problem in existing exhaust gas by-pass valve:
1, during engine cold-start, the default setting of exhaust gas by-pass valve 3 is for closing, engine exhaust can not be discharged via exhaust gas by-pass valve 3 runner, the catalyst converter in downstream can only be flowed into via turbo machine 4, because turbo machine 4 can absorb waste-gas heat, the exhaust gas temperature entering catalyst converter 5 can be cooled by turbo machine 4, and the medium in catalyst converter 5 can not be rapidly heated to operating temperature and play catalysis, and therefore engine cold-start discharges pollutants more;
2, motor is when low-load works, positive pressure pressure final controlling element 33 pilot pressure is also corresponding lower, be not enough to push cover plate valve valve gap 32 open, waste gas can not be discharged via bypass valve runner 31, can only flow to catalyst converter 5 by turbo machine runner, the air flue air pressure therefore between engine body and charger turbine 4 is higher, is unfavorable for the smooth combustion gas of motor, therefore motor additionally can consume a part of acting ability for exhaust, worsens fuel economy;
3, when motor needs to regulate air mass flow, rocking arm 35 and cover plate valve valve gap 32 rotation angle under final controlling element 33 drives, open exhaust gas by-pass valve runner 31.But the effective flow area of exhaust gas bypass runner is non-linear relevant to the angle that cover plate valve is opened.Meanwhile, exhaust gas pulse acts on the valve face of cover plate valve, can additionally increase or reduce valve gap stroke.Due to above-mentioned two reasons, bypass valve is stable not to air flow control;
4, during high engine load work, waste gas air pressure is higher, and because the stroke directions of cover plate valve valve gap 32 is identical with its waste gas gas pressure direction, valve gap promotes by waste gas, easily causes it to be not closed completely to exhaust gas bypass valve passage 31, reduces engine performance.Meanwhile, engine body 1 is interrupted exhaust and causes exhaust gas pressure dynamic fluctuation, and cover plate valve valve gap 32 easily produces shake by its effect, forms abnormal sound noise.
Summary of the invention
The object of the present invention is to provide a kind of exhaust gas by-pass valve of turbosupercharger, accelerate the cold start-up catalyst warm-up time, exhaust back pressure under reduction engine low load, improve the control accuracy in each load operation situation of motor, the sealing of exhaust gas by-pass valve under enhancing high engine load, reduces exhaust gas by-pass valve abnormal sound noise.
The exhaust gas by-pass valve of turbosupercharger of the present invention, described exhaust gas by-pass valve has the bypass flow channel be connected with air outlet by the suction port of described turbo machine and the spool that described bypass flow channel opening portion is opened or closed, described spool comprises valve stem part and is connected to the valve plate part on valve stem part, described valve stem part can move axially, to drive valve plate part along the translation of bypass flow channel opening portion end face, make valve plate part by described opening portion face opening or close.
Further, the valve stem part of described spool is by driver drives axial motion.
Further, described driver forms a valve open in usual with spool, and namely driver is when the default setting without external excitation, and described valve plate part keeps the state that the circulation of described bypass is opened.
Further, described driver comprises return spring and the pressure chamber split by diaphragm and piston cavity, external control pressure inputs in described pressure chamber, push rod in described piston cavity is connected with the valve stem part of described spool, described return spring is set on push rod, and it has the trend making described valve plate part keep relative bypass flow channel to open.
Further, there is guide plate in described bypass flow channel opening portion arranged outside, there is in the middle part of this guide plate the air passing hole just right with opening portion, formed between described guide plate and opening portion end face for described valve plate part along the guiding groove slided in it.
Adopt Rotary spool compared to existing exhaust gas by-pass valve, exhaust gas by-pass valve of the present invention adopts the spool open in usual of radial translation, has following advantage:
1, bypass valve default setting is for opening, during engine cold-start, engine exhaust can get around turbo machine, runner via exhaust gas by-pass valve flows into the catalyst converter in downstream, this can reduce the waste-gas heat that turbo machine absorbs, and makes the exhaust gas temperature entering catalyst converter higher, and the catalytic media being in the catalyst converter of cold conditions can shorten preheat time, catalyst converter can reach operating temperature sooner, and therefore can reduce pollution emissions thing.
2, motor is when low-load works, because bypass valve can be selected to open completely, increase engine exhaust circulation area, be conducive to the smooth combustion gas of motor, therefore compared to the design cannot opening bypass valve in prior art under this engine condition, the invention enables motor will be lacked by exhaust consumes acting, fuel economy is better.
3, when motor needs to regulate air mass flow, spool is straight line motion in guiding groove, and effective flow area that spool is opened is relevant to its stroke linear, and therefore flow control is closer to linearly, and control accuracy and accuracy obviously promote.Meanwhile, act on the exhaust gas pulse in valve plate part, its active force is mutually vertical with the moving direction of spool, and can not cause spool malfunction, therefore flow control is more stable.
4, during high engine load work, although waste gas air pressure is higher, but because valve core movement direction is mutually vertical with atmospheric pressure direction suffered by it, malfunction can not be produced because of exhaust gas pressure effect, bypass valve is to the better tightness of waste gas, can ensure that more waste gas streams is to turbo machine, utilize the energy of waste gas to improve the working power of gas compressor, help engine body to obtain more fresh air.Meanwhile, spool is spacing by guide groove structure, can not be subject to exhaust pulses effect malfunction or shake, can effectively avoid abnormal sound noise.
Accompanying drawing explanation
Fig. 1 is turbocharged engine system structure schematic diagram;
Fig. 2 is the structural representation of existing exhaust gas by-pass valve;
Fig. 3 is the structural representation of exhaust gas by-pass valve of the present invention;
Fig. 4 is the A-A sectional drawing of Fig. 3;
Fig. 5 is the plan view of described spool.
Embodiment
Below in conjunction with drawings and Examples, the present invention is further elaborated, and following examples only for explaining the present invention, do not form limiting the scope of the present invention.
The exhaust gas by-pass valve of the turbosupercharger shown in Fig. 3, described exhaust gas by-pass valve has the bypass flow channel 31 be connected with air outlet by the suction port of described turbo machine, the spool 36 that described bypass flow channel opening portion is opened or closed, and controls the driver 33 of spool movement.
See Fig. 5, described spool 36 comprises valve stem part 36a and is connected to the valve plate part 36b on valve stem part, in the present embodiment, valve plate part 36b is rectangular plate face shape, certain described valve plate part also can be polygonal or circular plate face, only need ensure after spool is closed completely, valve plate part 36b can block described opening portion completely.
Described driver 33 adopts positive pressure formula driver, and it is identical with working forms with the structure of existing driver, as patent CN101749104 and CN204003081 etc. disclose associated drive structure.Described driver 33 comprises return spring 33b and the pressure chamber 33c split by diaphragm and piston cavity 33d, external control pressure inputs in described pressure chamber, push rod 33a in described piston cavity is connected by pin 36c with the valve stem part 36b of described spool, and described return spring is set on push rod 33a.Described valve stem part 36a can be driven by described push rod 33a and move axially, to drive valve plate part 36b along the translation of bypass flow channel opening portion end face, make valve plate part by described opening portion face opening or close, the movement direction of valve plate part and bypass flow channel airflow direction near normal.Described return spring 33b is Compress Spring, and it has the trend driving push rod to move up.Therefore described driver 33 forms a valve open in usual with spool 36, namely the pressure chamber 33c of driver is when the default setting inputted without external excitation, under the effect of described return spring 33b, described valve plate part is moved, and keeps the state that bypass flow channel is opened.
See Fig. 4, outside described bypass flow channel opening portion, be also provided with guide plate 37, there is in the middle part of this guide plate the air passing hole 37a just right with opening portion, formed between described guide plate and opening portion end face for described valve plate part along the guiding groove 37b slided in it.
During above-mentioned exhaust gas by-pass valve work, under default setting, spool is in position shown in Fig. 3, and bypass flow channel 31 keeps unimpeded unlatching, and the waste gas of engine exhaust directly flows to the catalyst converter 5 in its downstream by bypass flow channel.Therefore, when visible motor is in cold start, the catalytic media in catalyst converter can be rapidly heated to operating temperature, plays catalysis.When motor is in idling or low load condition without the need to air intake pressurized, the bypass flow channel 31 of unimpeded unlatching can help motor to keep alap exhaust back pressure, thus improves fuel economy.
When motor need more high load time, the pilot pressure inputting described driver pressure chamber 33c raises, promote described push rod to move down, thus make valve plate part 36b turn down the sectional flow area of bypass flow channel opening portion, thus be reduced by the exhaust gas flow of exhaust gas by-pass valve, make more waste gas streams to turbo machine, increase turbine operating efficiency, and then increase the working efficiency of the gas compressor coaxial with it.
Claims (5)
1. an exhaust gas by-pass valve for turbosupercharger, described exhaust gas by-pass valve has the bypass flow channel (31) be connected with air outlet by the suction port of described turbo machine and the spool (36) that described bypass flow channel opening portion is opened or closed, and it is characterized in that:
Described spool comprises valve stem part (36a) and is connected to the valve plate part (36b) on valve stem part, described valve stem part can move axially, to drive valve plate part along the translation of bypass flow channel opening portion end face, make valve plate part by described opening portion face opening or close.
2. the exhaust gas by-pass valve of turbosupercharger according to claim 1, is characterized in that: the valve stem part of described spool drives axial motion by driver (33).
3. the exhaust gas by-pass valve of turbosupercharger according to claim 2, it is characterized in that: described driver forms a valve open in usual with spool, namely driver is when the default setting without external excitation, and described valve plate part keeps the state that the circulation of described bypass is opened.
4. the exhaust gas by-pass valve of the turbosupercharger according to Claims 2 or 3, it is characterized in that: described driver (33) comprises return spring (33b) and the pressure chamber (33c) split by diaphragm and piston cavity (33d), external control pressure inputs in described pressure chamber, push rod (33a) in described piston cavity is connected with the valve stem part of described spool, described return spring is set on push rod, and it has the trend making described valve plate part keep relative bypass flow channel to open.
5. the exhaust gas by-pass valve of turbosupercharger according to claim 1, it is characterized in that: have guide plate (37) in described bypass flow channel opening portion arranged outside, there is in the middle part of this guide plate the air passing hole (37a) just right with opening portion, formed between described guide plate and opening portion end face for described valve plate part along the guiding groove slided in it (37b).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510270887.0A CN104948295B (en) | 2015-05-26 | 2015-05-26 | A kind of exhaust gas by-pass valve of turbocharger |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510270887.0A CN104948295B (en) | 2015-05-26 | 2015-05-26 | A kind of exhaust gas by-pass valve of turbocharger |
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| CN104948295A true CN104948295A (en) | 2015-09-30 |
| CN104948295B CN104948295B (en) | 2018-05-01 |
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| CN201510270887.0A Active CN104948295B (en) | 2015-05-26 | 2015-05-26 | A kind of exhaust gas by-pass valve of turbocharger |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106640348A (en) * | 2015-10-28 | 2017-05-10 | 长城汽车股份有限公司 | Waste gas bypass valve structure of supercharger and waste gas bypass valve of supercharger |
| CN109563767A (en) * | 2017-03-30 | 2019-04-02 | 三菱重工发动机和增压器株式会社 | Exhaust bypass device and booster |
| CN112682166A (en) * | 2020-12-18 | 2021-04-20 | 合肥工业大学 | Multistage control device of turbocharger |
| EP4008891A3 (en) * | 2020-12-01 | 2022-08-24 | Langlechner GmbH & Co. KG | Combined heat and power plant and shut-off device for a combined heat and power plant |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6488259B1 (en) * | 1999-02-09 | 2002-12-03 | Mitsubishi Denki Kabushiki Kaisha | Valve device |
| CN201747485U (en) * | 2010-08-17 | 2011-02-16 | 无锡隆盛科技有限公司 | Electric EGR valve |
| JP2012251615A (en) * | 2011-06-03 | 2012-12-20 | Isuzu Motors Ltd | Flow passage switching valve, internal combustion engine, and egr method of internal combustion engine |
-
2015
- 2015-05-26 CN CN201510270887.0A patent/CN104948295B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6488259B1 (en) * | 1999-02-09 | 2002-12-03 | Mitsubishi Denki Kabushiki Kaisha | Valve device |
| CN201747485U (en) * | 2010-08-17 | 2011-02-16 | 无锡隆盛科技有限公司 | Electric EGR valve |
| JP2012251615A (en) * | 2011-06-03 | 2012-12-20 | Isuzu Motors Ltd | Flow passage switching valve, internal combustion engine, and egr method of internal combustion engine |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106640348A (en) * | 2015-10-28 | 2017-05-10 | 长城汽车股份有限公司 | Waste gas bypass valve structure of supercharger and waste gas bypass valve of supercharger |
| CN106640348B (en) * | 2015-10-28 | 2019-03-26 | 长城汽车股份有限公司 | Booster exhaust gas bypass valve arrangement and booster exhaust gas by-pass valve |
| CN109563767A (en) * | 2017-03-30 | 2019-04-02 | 三菱重工发动机和增压器株式会社 | Exhaust bypass device and booster |
| CN109563767B (en) * | 2017-03-30 | 2021-01-15 | 三菱重工发动机和增压器株式会社 | Exhaust bypass device and supercharger |
| EP4008891A3 (en) * | 2020-12-01 | 2022-08-24 | Langlechner GmbH & Co. KG | Combined heat and power plant and shut-off device for a combined heat and power plant |
| CN112682166A (en) * | 2020-12-18 | 2021-04-20 | 合肥工业大学 | Multistage control device of turbocharger |
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| Publication number | Publication date |
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| CN104948295B (en) | 2018-05-01 |
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