CN102022180B - Exhaust gas turbocharger arrangement, attached driving system and design method of driving system - Google Patents
Exhaust gas turbocharger arrangement, attached driving system and design method of driving system Download PDFInfo
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- CN102022180B CN102022180B CN201010282826.3A CN201010282826A CN102022180B CN 102022180 B CN102022180 B CN 102022180B CN 201010282826 A CN201010282826 A CN 201010282826A CN 102022180 B CN102022180 B CN 102022180B
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- exhaust
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- 238000000034 method Methods 0.000 title abstract description 11
- 238000004064 recycling Methods 0.000 abstract 1
- 239000007789 gas Substances 0.000 description 86
- 239000012530 fluid Substances 0.000 description 63
- 239000002912 waste gas Substances 0.000 description 49
- 238000002485 combustion reaction Methods 0.000 description 27
- 230000006835 compression Effects 0.000 description 25
- 238000007906 compression Methods 0.000 description 25
- 230000009467 reduction Effects 0.000 description 8
- 230000002000 scavenging effect Effects 0.000 description 6
- 230000007246 mechanism Effects 0.000 description 4
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 238000005265 energy consumption Methods 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000004140 cleaning Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 239000000295 fuel oil Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/52—Systems for actuating EGR valves
- F02M26/59—Systems for actuating EGR valves using positive pressure actuators; Check valves therefor
- F02M26/61—Systems for actuating EGR valves using positive pressure actuators; Check valves therefor in response to exhaust pressure
- F02M26/615—Systems for actuating EGR valves using positive pressure actuators; Check valves therefor in response to exhaust pressure the exhaust back pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/09—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/51—EGR valves combined with other devices, e.g. with intake valves or compressors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2220/00—Application
- F05B2220/40—Application in turbochargers
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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)
- Exhaust-Gas Circulating Devices (AREA)
Abstract
The invention relates to an exhaust gas turbocharger arrangement,attached driving system and design method of driving system. The exhaust gas turbocharger arrangement has an exhaust gas turbocharger with an exhaust gas turbine, which is arranged in an exhaust gas tract of the exhaust gas turbocharger arrangement. A compressor stays in rotary drive connection with the exhaust gas turbine. An exhaust gas recycling device comprises an exhaust gas inlet position, which is placed in a fluidic compressing path in the compressor, so that exhaust gas is compressed by simply comparing a pressure difference between an inlet pressure of the exhaust gas in the fluidic compressing path and a charging air pressure of the inlet pressure.
Description
Technical field
The present invention relates to a kind ofly according to the exhaust-gas turbocharger device as described in the preamble of claim 1, be equipped with the drive system of this exhaust-gas turbocharger device and the method for design driven system.
Background technique
By the exhaust-gas turbocharger device of DE 2,006 055 814 A1 and the described type of the DE known beginning of 10 2,005 015 151 A1.
For particularly at its NO
xdischarge aspect meets the waste gas limit value in the future of internal-combustion engine, uses more and more the exhaust-gas turbocharger device with waste gas feedback or EGR.Relate at this: the waste gas of internal-combustion engine mixes with the pressurized air for internal-combustion engine.
In waste gas feeds back, conventionally must overcome the pressure reduction between " scavenging drop ", i.e. pressure in charge air duct and the pressure in exhaust piping, for example use independent fan or waste gas before the compressor of corresponding exhaust-gas turbocharger device, to be mixed into pressurized air system for this reason.In any case, in order to overcome scavenging drop, needing significant energy consumption, it may damage the efficiency of exhaust-gas turbocharger device.
Summary of the invention
Therefore the object of the invention is: a kind of exhaust-gas turbocharger device is provided, wherein reduces or reduce the energy consumption that is passed to the waste gas streams of pressurized air system for compression and back.In addition the object of the invention is: provide a kind of and be equipped with the drive system of this exhaust-gas turbocharger device and for designing the method for this drive system.
Above-mentioned purpose realizes by exhaust-gas turbocharger device according to claim 1, drive system according to claim 7 or method according to claim 8.Improvement project of the present invention provides in the dependent claims.
According to a first aspect of the invention, a kind of exhaust-gas turbocharger device for internal-combustion engine, it comprises exhaust-gas turbocharger, exhaust-gas turbocharger has exhaust turbine, described exhaust turbine is arranged in the waste gas system that waste gas outlet fluid exhaust-gas turbocharger device and internal-combustion engine is connected, wherein exhaust-gas turbocharger also has with exhaust turbine and rotarilys actuate the compressor being connected, and described compressor is arranged in the pressurized air system that air inlet fluid exhaust-gas turbocharger device and internal-combustion engine is connected; Exhaust-gas turbocharger device also comprises Exhaust gas recirculation device, it has with waste gas is the entrance that is connected of fluid and is the outlet that fluid is connected with pressurized air, thereby is that the waste gas separating can enter in pressurized air system in waste gas in-position via outlet from waste gas.
According to the feature of exhaust-gas turbocharger device of the present invention be: waste gas in-position is arranged in the fluid compression circuit of compressor, thereby the waste gas in inflow compressor enters the pressure reduction between the boost pressure that enters pressure and will realize in fluid compression circuit in the case of being only equilibrated at waste gas, is directly compressed into by entering pressure the boost pressure that will realize.
In other words, for balance or overcome the merit of the pressure reduction between the boost pressure that enters pressure and will realize of waste gas or can energy be delivered to exactly waste gas.
According to the present invention, be only that the qualifying part of compressor loads waste gas partly, it is yet in the region in less centrifugal force load or even in the guiding blade system of compressor.
Therefore the energy charge of transporting to the waste gas of pressurized air system for compression and back can be reduced or reduce, the efficiency of exhaust-gas turbocharger device can be improved thus.
Therefore for particularly at its NO
xdischarge aspect meets the waste gas limit value in the future of internal-combustion engine, a kind of have waste gas feedback or exhaust-gas turbocharger device EGR, efficiency optimization are provided, and it particularly can also be for the two stroke engine of slowly operation and the four stroke engine of moving fast in heavy oil operation state.
A kind of mode of execution of exhaust-gas turbocharger device according to the present invention, exhaust gas entrance position is between the impeller fluid input of compressor and the diffuser fluid output of compressor.
The pressure that this region in the fluid compression circuit of compressor is essentially in compressor is set up region, thereby by that select to be applicable to and the exhaust gas entrance position that enters pressure and compressor characteristics curvilinear correlation waste gas, can reduce best or reduce merit or energy for compressed exhaust gas.
A kind of mode of execution of exhaust-gas turbocharger device according to the present invention, exhaust gas entrance position is between the impeller fluid input of compressor and the rear guide mechanism fluid output of compressor.
The another kind of mode of execution of exhaust-gas turbocharger device according to the present invention, exhaust gas entrance position is between the impeller fluid input of compressor and the impeller fluid output of compressor.
If pressure reduction or scavenging drop are higher, such exhaust gas entrance position is particularly advantageous.
The another kind of mode of execution of exhaust-gas turbocharger device according to the present invention, exhaust gas entrance position is between the impeller fluid output of compressor and the diffuser fluid output of compressor.
If for example in two stroke engine, pressure reduction or scavenging drop are lower, such exhaust gas entrance position is particularly advantageous.
The another kind of mode of execution of exhaust-gas turbocharger device according to the present invention, the entrance of described Exhaust gas recirculation device is that fluid is connected at waste gas branch location place with waste gas, before wherein said waste gas branch location is positioned at turbine inlet along waste gas system.
This waste gas branch location has been guaranteed: waste gas to enter pressure high as far as possible, and then scavenging drop differential pressure is low as far as possible.
The another kind of mode of execution of exhaust-gas turbocharger device according to the present invention, Exhaust gas recirculation device can have gaseous effluent and/or exhaust scrubber.
In other words, can, after " before cylinder " is mixed to the fluid compression circuit that is arranged in compressor of pressurized air system, is cooled if desired and cleans by " after the cylinder " or " before exhaust turbine " of internal-combustion engine from the waste gas of waste gas system.
According to a second aspect of the invention, the drive system with exhaust-gas turbocharger device and internal-combustion engine is provided, wherein exhaust-gas turbocharger device is implemented according to one of the present invention, multiple or all aforementioned definite embodiments in each imaginabale combination, wherein the waste gas of exhaust-gas turbocharger device system is connected with the waste gas outlet fluid of internal-combustion engine, and the pressurized air system of exhaust-gas turbocharger device is connected with the air inlet fluid of internal-combustion engine.
According to a third aspect of the invention we, provide a kind of method for design consideration drive system of the present invention, wherein said method at least comprises the following steps: to determine the exhaust gas pressure indicatrix that depends on load of internal-combustion engine; Determine the boost pressure indicatrix that depends on load of compressor; Determine for example average operating load (for example engine loading should mainly use it to drive internal-combustion engine) of internal-combustion engine; Determine the pressure reduction based on operating load between exhaust gas pressure indicatrix and boost pressure indicatrix; Determine that according to the extension position based on compression line length in fluid compression circuit the pressure of compressor characteristics sets up indicatrix; Determine the extension position in fluid compression circuit, the pressure that can be realized by compressor is based upon this extension position place and equals the definite pressure reduction between exhaust gas pressure indicatrix and boost pressure indicatrix; Determine exhaust gas entrance position, thereby exhaust gas entrance position and definite extension position are corresponding.
Last inventor recognizes: because waste gas before exhaust turbine at higher stress level, only must find a place or position (exhaust gas entrance position), raise can be until reach boost pressure level for residual pressure herein.
According to the embodiment of the present invention, exhaust gas entrance position is for example covered on profile to being located at before impeller fluid output in radial compressor after impeller fluid input.In the time of corresponding less scavenging drop, as in two stroke engine, exhaust gas entrance position can be between impeller fluid output and diffuser fluid output, because also improve there static pressure.
Brief description of the drawings
Below by preferred embodiment and be described in detail with reference to the attached drawings the present invention.
Fig. 1 illustrates according to the schematic diagram of the drive system of the embodiment of the present invention.
Fig. 2 illustrates according to the partial schematic diagram of the compressor of the exhaust-gas turbocharger device of the drive system of the embodiment of the present invention.
Fig. 3 illustrates the partial enlarged drawing that is similar to Fig. 2 of the compressor of the exhaust-gas turbocharger device of drive system according to an embodiment of the invention.
Fig. 4 illustrates a chart, wherein show to according to the relevant exhaust gas pressure indicatrix of the engine loading of the drive system of the embodiment of the present invention and boost pressure indicatrix.
Fig. 5 illustrates a chart, wherein, according to according to the extension position based on compression line length in the fluid compression circuit of the compressor of the exhaust-gas turbocharger device of the drive system of the embodiment of the present invention, illustrates that the pressure of compressor characteristics is set up indicatrix.
Reference numerals list
1 drive system
10 exhaust-gas turbocharger devices
20 exhaust-gas turbochargers
21 exhaust turbines
21a turbine inlet
21b turbine outlet
22 exhaust pipings
23 exhaust ducts
25 coupling shafts
26 compressors
26a suction port of compressor
26b compressor outlet
260 housings
261 impellers
262 impeller blades
263 impeller fluid inputs
264 impeller fluid outputs
265 diffusers
266 diffuser fluid outputs
267 helical ducts
268 rear guide mechanisms
27 fresh air pipes
28 admission lines
29 admission lines
30 Exhaust gas recirculation device
30a entrance
30b outlet
40 charger-air coolers
60 internal-combustion engines
60a air inlet
60b waste gas outlet
AE exhaust gas entrance position
VP fluid compression circuit
A the first boundary
B the second boundary
P pressure
PA exhaust gas pressure
PL boost pressure
Δ P pressure reduction
L engine loading
AL operating load
A waste gas
Embodiment
Fig. 1 illustrates according to the schematic diagram of the drive system 1 of the embodiment of the present invention.
Drive system 1 has an exhaust-gas turbocharger device 10 and and is for example designed to internal-combustion engine 60 diesel engine and/or gas engine and that be connected with exhaust-gas turbocharger device 10.
Exhaust-gas turbocharger device 10 has exhaust-gas turbocharger 20, Exhaust gas recirculation device 30 and charger-air cooler 40.
The exhaust turbine 21 and one that exhaust-gas turbocharger 20 has with turbine inlet 21a and turbine outlet 21b rotarilys actuate with exhaust turbine 21 compressor 26 being connected by coupling shaft 25, and described compressor 26 has suction port of compressor 26a and compressor outlet 26b.
Suction port of compressor 26a sets up fluid with fresh air pipe 27 and is connected, thereby fresh air for example can be transported to compressor 26 by fresh air pipe 27 from atmosphere.
Exhaust gas recirculation device 30 can be designed with waste gas cleaning plant (not shown) and gaseous effluent (not shown) and applicable controlling device, and have: an entrance 30a, this entrance is connected (at waste gas branch location place) before turbine inlet 21a with exhaust piping 22 fluids; One outlet 30b, this outlet is connected with compressor 26 fluids.
Shown at Fig. 2 and Fig. 3, the compressor 26 that is designed to radial compressor at this has housing 260 and and is fixed on the impeller 261 on the coupling shaft 25 can be rotated to support in housing 260, and described impeller has multiple impeller blades 262.
More precisely, fluid compression circuit VP extends to diffuser fluid output 266 from impeller fluid input 263 via the radial clearance of impeller fluid output 264 and formation diffuser 265, described diffuser fluid output 266 passes in housing 260 in the shaped spiral housing forming, have helical duct 267, and described helical duct 267 is connected with compressor outlet 26b fluid itself.Guide mechanism or guiding leaf grating 268 after can arranging in diffuser 265.
As Fig. 1 to Fig. 3 illustrate, the outlet 30b of Exhaust gas recirculation device 30 is so that fluid is connected with pressurized air, making from waste gas is that the waste gas A separating can enter in pressurized air system in exhaust gas entrance position AE (referring to Fig. 3) via outlet 30b, enters more precisely in fluid compression circuit VP.
As stated in the beginning, waste gas A has the exhaust gas pressure PA relevant to the engine loading L of internal-combustion engine 60, and waste gas A utilizes this exhaust gas pressure to enter pressurized air system, and this exhaust gas pressure is shown as the pressure that enters of waste gas A there.Equally as stated in the beginning, exhaust gas pressure PA is less than the boost pressure PL that will utilize compressor 26 to realize as internal-combustion engine 60 in admission line 28,29 or at the air inlet 60a place of internal-combustion engine 60 taking pressure differential deltap P conventionally.This correlation is shown in Figure 4, wherein at boost pressure PL indicatrix shown in the chart of the pressure P relevant to the engine loading L of internal-combustion engine 60 and exhaust gas pressure PA indicatrix.
Fig. 5 illustrates a chart, wherein according to (from the first boundary a to the second boundary extension position b), illustrate that the pressure of compressor characteristics is set up indicatrix at this based on compression line length in the fluid compression circuit VP of compressor 26.Shown in from Fig. 5, pressure is set up indicatrix and is walked to have backward almost linear trend in initial curvilinerar figure.Can draw thus: the stroke of the fluid that compress process in fluid compression circuit VP is larger, and the pressure forming is larger.But curve shown in Figure 5 has only been shown pressure trend in principle.
The regulation according to the present invention now: exhaust gas entrance position AE is so arranged in the fluid compression circuit VP in compressor 26, thus the waste gas A (as illustrated by the thick arrow in Fig. 3) that flows into compressor 26 enters the pressure differential deltap P (referring to Fig. 4) between the boost pressure PL that enters pressure (exhaust gas pressure PA) and will realize in fluid compression circuit VP and is directly compressed into the boost pressure PL that will realize by entering pressure in the case of being only equilibrated at waste gas A.
According to embodiments of the invention, in the most general mode, exhaust gas entrance position AE is between the impeller fluid input 263 of compressor 26 and the diffuser fluid output 266 of compressor 26.According to another embodiment of the present invention, in special a little mode, exhaust gas entrance position AE can be between the fluid output of the rear guide mechanism 268 of the impeller fluid input 263 of compressor 26 and compressor 26.
The embodiment shown in Figure 3 according to the present invention, exhaust gas entrance position AE is between the impeller fluid input 263 of compressor 26 and the impeller fluid output 264 of compressor 26.
According to unshowned embodiment of the present invention, exhaust gas entrance position AE can also be between the impeller fluid output 264 of compressor 26 and the diffuser fluid output 266 of compressor 26.
Described in above, at least comprise the following steps: to determine the exhaust gas pressure PA indicatrix that depends on load of internal-combustion engine 60 for the method for design consideration drive system 1 of the present invention, determine the boost pressure PL indicatrix that depends on load of compressor 26; Determine the operating load AL (for example engine loading L should mainly use it to drive internal-combustion engine 60) of internal-combustion engine 60; Determine (as shown in Figure 4) between exhaust gas pressure PA indicatrix and boost pressure PL indicatrix pressure differential deltap P based on operating load; Determine that according to the extension position based on compression line length (a to b in Fig. 2) in fluid compression circuit VP the pressure of compressor characteristics sets up indicatrix (as shown in fig. 5); Determine the extension position in fluid compression circuit VP, the pressure that can be realized by compressor 26 is based upon this extension position place and equals the definite pressure differential deltap P between exhaust gas pressure PA indicatrix and boost pressure PL indicatrix; Determine exhaust gas entrance position AE, thereby exhaust gas entrance position AE and definite extension position (as shown in Figure 3) are corresponding.
Claims (7)
1. for the method for design driven system (1), described drive system has internal-combustion engine (60) and exhaust-gas turbocharger device (10),
Wherein, described exhaust-gas turbocharger device (10) comprising:
Exhaust-gas turbocharger (20), it has exhaust turbine (21), and described exhaust turbine is arranged in the waste gas system being connected with waste gas outlets internal-combustion engine (60) (60b) fluid exhaust-gas turbocharger device (10); Exhaust-gas turbocharger (20) also has with exhaust turbine (21) and rotarilys actuate the compressor (26) being connected, described compressor is arranged in the pressurized air system being connected with air inlets internal-combustion engine (60) (60a) fluid exhaust-gas turbocharger device (10), and
Exhaust gas recirculation device (30), it has with waste gas is the entrance (30a) that is connected of fluid and is the outlet (30b) that fluid is connected with pressurized air, thereby be that the waste gas (A) separating can enter in pressurized air system at waste gas in-position (AE) via outlet (30b) from waste gas
Wherein, described waste gas in-position (AE) is arranged in the fluid compression circuit (VP) of compressor (26), thereby the waste gas (A) flowing in compressor (26) enters the pressure reduction (△ P) between the boost pressure (PL) that enters pressure and will realize in fluid compression circuit (VP) in the case of being only equilibrated at waste gas (A), directly be compressed into by entering pressure the boost pressure (PL) that will realize
Wherein, the entrance (30a) of described Exhaust gas recirculation device (30) is that fluid is connected at waste gas branch location place with waste gas, and wherein, described waste gas branch location is positioned at turbine inlet (21a) before along waste gas system,
It is characterized in that,
Said method comprising the steps of:
Determine the exhaust gas pressure that depends on load (PA) indicatrix of internal-combustion engine (60),
Determine the boost pressure that depends on load (PL) indicatrix of compressor (26),
Determine the operating load (AL) of internal-combustion engine (60),
Determine the pressure reduction based on operating load (AL) (△ P) between exhaust gas pressure (PA) indicatrix and boost pressure (PL) indicatrix,
According in fluid compression circuit (VP) based on compression line length (extension position of a → b) determines that the pressure of compressor characteristics sets up indicatrix,
Determine the extension position in fluid compression circuit (VP), the pressure that can be realized by compressor (26) is based upon this extension position place and equals the definite pressure reduction (△ P) between exhaust gas pressure (PA) indicatrix and boost pressure (PL) indicatrix, and
Determine exhaust gas entrance position (AE), thereby exhaust gas entrance position (AE) is corresponding with definite extension position.
2. according to the drive system (1) designing by method claimed in claim 1, described drive system has exhaust-gas turbocharger device (10) and internal-combustion engine (60), the waste gas system of wherein said exhaust-gas turbocharger device (10) is connected with waste gas outlet (60b) fluid of internal-combustion engine (60), and the pressurized air of described exhaust-gas turbocharger device (10) system is connected with air inlet (60a) fluid of described internal-combustion engine (60).
3. one kind for by the exhaust-gas turbocharger device (10) of the internal-combustion engine (60) of drive system claimed in claim 2.
4. exhaust-gas turbocharger device according to claim 3 (10), wherein, described waste gas in-position (AE) is positioned between the impeller fluid input (263) of compressor (26) and the diffuser fluid output (266) of compressor (26).
5. exhaust-gas turbocharger device according to claim 4 (10), wherein, described exhaust gas entrance position (AE) is positioned between the impeller fluid input (263) of compressor (26) and the fluid output of the rear guide mechanism (268) of compressor (26).
6. exhaust-gas turbocharger device according to claim 4 (10), wherein, described exhaust gas entrance position (AE) is positioned between the impeller fluid input (263) of compressor (26) and the impeller fluid output (264) of compressor (26).
7. exhaust-gas turbocharger device according to claim 4 (10), wherein, described exhaust gas entrance position (AE) is positioned between the impeller fluid output (264) of compressor (26) and the diffuser fluid output (266) of compressor (26).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102009041223.9A DE102009041223B4 (en) | 2009-09-11 | 2009-09-11 | Method for designing a drive system |
| DE102009041223.9 | 2009-09-11 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102022180A CN102022180A (en) | 2011-04-20 |
| CN102022180B true CN102022180B (en) | 2014-06-18 |
Family
ID=43603307
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010282826.3A Expired - Fee Related CN102022180B (en) | 2009-09-11 | 2010-09-10 | Exhaust gas turbocharger arrangement, attached driving system and design method of driving system |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JP5313981B2 (en) |
| KR (1) | KR101605912B1 (en) |
| CN (1) | CN102022180B (en) |
| CH (1) | CH701782B1 (en) |
| DE (1) | DE102009041223B4 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103541811A (en) * | 2012-07-09 | 2014-01-29 | 北汽福田汽车股份有限公司 | Exhaust gas recirculation system, automobile with system and exhaust gas recirculation method |
| JP6388772B2 (en) | 2014-02-25 | 2018-09-12 | 三菱重工業株式会社 | Centrifugal compressor and diffuser manufacturing method |
| DE102017117783A1 (en) * | 2017-08-04 | 2019-02-07 | Man Diesel & Turbo Se | Turbine inlet housing of an axial turbine of a turbocharger |
| DE102017221717A1 (en) * | 2017-12-01 | 2019-06-06 | Man Energy Solutions Se | centrifugal compressors |
| CN108730073A (en) * | 2018-03-26 | 2018-11-02 | 北京理工大学 | A kind of high-pressure exhaust-gas recirculation system of supercharged diesel engine engine |
| CN114294670A (en) * | 2021-12-31 | 2022-04-08 | 先之科半导体科技(东莞)有限公司 | Automatic processing equipment for processing materials of power MOS (metal oxide semiconductor) tube |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3139158B2 (en) * | 1992-08-24 | 2001-02-26 | 石川島播磨重工業株式会社 | Exhaust recirculation device |
| JP2676300B2 (en) * | 1992-11-02 | 1997-11-12 | 日野自動車工業株式会社 | Exhaust gas recirculation system for turbocharged engine |
| DE10244535A1 (en) * | 2002-09-25 | 2004-04-08 | Daimlerchrysler Ag | Internal combustion engine with a compressor in the intake tract |
| DE102005015151A1 (en) | 2005-03-31 | 2006-10-26 | Alstom Technology Ltd. | Gas turbine system for power station, has control device to control volume flow and/or temperature of combustion exhaust gas, such that fresh gas-exhaust gas-mixture entering into compressor of turbo group has preset reference temperature |
| DE102006055814B4 (en) | 2006-11-27 | 2017-06-01 | Ford Global Technologies, Llc | Turbocharged combustion engine with exhaust gas recirculation |
| JP2008309125A (en) * | 2007-06-18 | 2008-12-25 | Toyota Motor Corp | Exhaust gas recirculation system for internal combustion engine |
-
2009
- 2009-09-11 DE DE102009041223.9A patent/DE102009041223B4/en not_active Expired - Fee Related
-
2010
- 2010-07-15 CH CH01152/10A patent/CH701782B1/en not_active IP Right Cessation
- 2010-08-31 JP JP2010193685A patent/JP5313981B2/en not_active Expired - Fee Related
- 2010-09-03 KR KR1020100086723A patent/KR101605912B1/en not_active Expired - Fee Related
- 2010-09-10 CN CN201010282826.3A patent/CN102022180B/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN102022180A (en) | 2011-04-20 |
| KR20110028227A (en) | 2011-03-17 |
| CH701782B1 (en) | 2014-09-15 |
| DE102009041223B4 (en) | 2014-01-02 |
| JP2011058490A (en) | 2011-03-24 |
| DE102009041223A1 (en) | 2011-03-24 |
| CH701782A2 (en) | 2011-03-15 |
| JP5313981B2 (en) | 2013-10-09 |
| KR101605912B1 (en) | 2016-03-23 |
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