CN1877099A - Internal combustion engine - Google Patents
Internal combustion engine Download PDFInfo
- Publication number
- CN1877099A CN1877099A CNA2006100945533A CN200610094553A CN1877099A CN 1877099 A CN1877099 A CN 1877099A CN A2006100945533 A CNA2006100945533 A CN A2006100945533A CN 200610094553 A CN200610094553 A CN 200610094553A CN 1877099 A CN1877099 A CN 1877099A
- Authority
- CN
- China
- Prior art keywords
- power plant
- hydraulic press
- exhaust
- gas turbocharger
- internal
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 60
- 239000000446 fuel Substances 0.000 claims abstract description 8
- 230000008878 coupling Effects 0.000 claims description 43
- 238000010168 coupling process Methods 0.000 claims description 43
- 238000005859 coupling reaction Methods 0.000 claims description 43
- 239000003921 oil Substances 0.000 claims description 28
- 239000002828 fuel tank Substances 0.000 claims description 10
- 239000010773 plant oil Substances 0.000 claims description 10
- 238000006073 displacement reaction Methods 0.000 claims description 2
- 230000002706 hydrostatic effect Effects 0.000 abstract 4
- 239000007789 gas Substances 0.000 description 35
- 239000002912 waste gas Substances 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
- F02B41/02—Engines with prolonged expansion
- F02B41/10—Engines with prolonged expansion in exhaust turbines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/14—Control of the alternation between or the operation of exhaust drive and other drive of a pump, e.g. dependent on speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
- F02B37/10—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump at least one pump being alternatively or simultaneously driven by exhaust and other drive, e.g. by pressurised fluid from a reservoir or an engine-driven pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
- F02B37/10—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump at least one pump being alternatively or simultaneously driven by exhaust and other drive, e.g. by pressurised fluid from a reservoir or an engine-driven pump
- F02B37/105—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump at least one pump being alternatively or simultaneously driven by exhaust and other drive, e.g. by pressurised fluid from a reservoir or an engine-driven pump exhaust drive and pump being both connected through gearing to engine-driven shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/02—Drives of pumps; Varying pump drive gear ratio
- F02B39/08—Non-mechanical drives, e.g. fluid drives having variable gear ratio
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
Abstract
The invention relates the combustion engine. The machine has a propulsion unit (11), the propulsion unit uses fuel, and the power produced by fuel is put in driving axle (12) of propulsion unit (11). The machine has an exhaust-driven turbo-charger (13), which makes the exhaust air from propulsion unit (11) reduce pressure in turbomachine to get power to send the burning air-flow in propulsion unit, the exhaust-driven turbo-charger rotor composed by a turbine rotor and a compresser rotor is coupled with the first hydrostatic machine (15), the driving axle (12) of propulsion unit (11) is coupled with the second hydrostatic machine (17), and the first hydrostatic machine (15) is coupled with the second hydrostatic machine (17) through oil pipe of propulsion unit return circuit at the condition of connecting a propulsion unit oil tank (18).
Description
Technical field
The present invention relates to a kind of exhaust gas turbocharger internal combustion engine.
Background technique
Known in order to improve working efficiency of internal combustion engine by prior art, internal-combustion engine is equipped with an exhaust-gas turbocharger.The waste gas of being discharged by power plant when waste gas supercharging or turbosupercharging reduces pressure in a turbo machine of exhaust-gas turbocharger, wherein the turbine drives exhaust-gas turbocharger compressor compresses the combustion air that is transported to power plant in this compressor.Between the compressor of exhaust-gas turbocharger and power plant, be connected a charger-air cooler, be used to make the combustion air of compression to be cooled to a definite temperature.Can improve the working efficiency of internal-combustion engine by such waste gas supercharging or turbosupercharging.
Exhaust-gas turbocharger can have high like this working efficiency, makes exhaust-gas turbocharger that an excess power is provided, and it for the combustion air ratio that produces a best in internal combustion engine power plant not necessarily.In order to utilize this excess power known by DE 35 32 938 C1, oil hydraulic motor of coupling connection is used to make the excess power that is provided by exhaust-gas turbocharger to convert driving power on an oil hydraulic pump of coupling connection and a live axle at internal-combustion engine on the exhaust-gas turbocharger.DE 35 32 938 C1 suggestion in addition, in the running state that the exhaust energy of internal-combustion engine lacks, make with the oil hydraulic pump of exhaust-gas turbocharger coupling connection remove with the coupling connection of the oil hydraulic motor of live axle coupling connection and make oil hydraulic pump pass through the service pump of an electric motor drive as motor operation.
Summary of the invention
Proposing the problem to be solved in the present invention thus is, realizes the internal combustion engine with simple structure.
Have power plant according to internal-combustion engine of the present invention, this power plant combustion fuel and join a live axle the inside of power plant by the power that combustion fuel produces, this internal-combustion engine also has an exhaust-gas turbocharger, it reduces pressure the exhaust flow that leaves motor of the internal-combustion engine and makes thus obtained power to be transported to the combustion air flow in the power plant and to be added into compressor the inside in order to compress in a turbo machine, one of them is by a turbine rotor and an exhaust-gas turbocharger rotor and one the first hydraulic press coupling connection that compressor drum constitutes of exhaust-gas turbocharger, and wherein the live axle of power plant also joins with the second hydraulic press coupling.During load operation when power plant are positioned at power plant loads higher extreme value with one more than, should in a generator duty (Generatorbetrieb) of same hydraulic press, from the exhaust-gas turbocharger rotor, take out mechanical work by first hydraulic press and convert the hydraulic pressure merit to, and then this hydraulic pressure merit be converted to mechanical work and joined the live axle the inside by second hydraulic press with live axle coupling connection in a dynamically working system of same hydraulic press with exhaust-gas turbocharger rotor coupling connection.During load operation when power plant are positioned at power plant loads low extreme value with one below, second hydraulic press that should join by the live axle coupling with power plant takes out mechanical work and converts the hydraulic pressure merit to from live axle in a generator duty of same hydraulic press, then this hydraulic pressure merit is converted to mechanical work and joined the exhaust-gas turbocharger the inside by first hydraulic press with exhaust-gas turbocharger rotor coupling connection in a dynamically working system of same hydraulic press.With first hydraulic press of exhaust-gas turbocharger rotor coupling connection with is connected in the centre respectively with second hydraulic press of live axle coupling connection that the oil pipe coupling by a power plant oil return line joins under the condition of a power plant fuel tank.
Therefore for according to first hydraulic press of internal-combustion engine of the present invention and exhaust-gas turbocharger coupling connection and with second hydraulic press of live axle coupling connection being positioned at the running state more than the power plant load higher extreme value but also all joining not only at internal-combustion engine with the power plant fuel tank coupling of power plant oil return line and power plant oil return line in the running state that is positioned at below the power plant load low extreme value of internal-combustion engine.On meaning of the present invention, can save according to the prior art of DE 35 32 938 C1 required independently hydraulic tubing and service pump.Can obviously simplify Structure of Internal-Combustion Engine thus.By utilizing the power plant oil return line to make exhaust-gas turbocharger and live axle hydraulic pressure coupling connection realize one of internal-combustion engine very compact structure form.
Provide advantageous modification of the present invention by dependent claims and following description.Describe embodiments of the invention in detail by means of accompanying drawing, but be not limited to these embodiments.In the accompanying drawing:
Description of drawings
Fig. 1 illustrates one according to internal-combustion engine of the present invention with schematic representation, according to power plant that more than power plant load higher extreme value, move of the first embodiment of the present invention,
Fig. 2 illustrates the internal-combustion engine of Fig. 1, power plant that below power plant load low extreme value, move,
Fig. 3 illustrates one according to internal-combustion engine of the present invention with schematic representation, according to the second embodiment of the present invention, and power plant that more than power plant load higher extreme value, move,,
Fig. 4 illustrates the internal-combustion engine of Fig. 3, power plant that move below power plant load low extreme value.
Embodiment
Describe the present invention in detail by means of Fig. 1 to Fig. 4 below.
Fig. 1 and 2 illustrates first embodiment according to internal-combustion engine 10 of the present invention with two different running statees.This internal-combustion engine 10 has power plant 11, wherein this power plant 11 combustion fuels and will be joined the bent axle or live axle 12 the insides of power plant 11 by the power that combustion fuel produces.This internal-combustion engine 10 also has an exhaust-gas turbocharger 13, and wherein this exhaust-gas turbocharger 13 has a turbo machine and a compressor.Make the exhaust flow decompression of the power plant 11 that leave internal-combustion engine 10 in the turbo machine of exhaust-gas turbocharger 13, wherein thus obtained power delivery is used to compress the combustion air flow that is transported to power plant 11 to the compressor of exhaust-gas turbocharger.A turbine rotor and a compressor drum of this turbosupercharger 13 pass through the exhaust-gas turbocharger rotor that an axle coupling joins and constitute exhaust-gas turbocharger 13.
On exhaust-gas turbocharger 13, join one first hydraulic press 15 according to Fig. 1 and 2 by clutch 14 couplings.Join one second hydraulic press 17 by clutch 16 couplings on the live axle 12 of these external power plant 11.Two hydraulic presses 15 and 17 not only can in the generator duty, move but also can in dynamically working system, move and with the power plant fuel tank 18 of a power plant oil return line of internal-combustion engine 10 by oil pipe 19 to 21 (see figure 1)s or 22 to 24 (see figure 2) couplings connection.
Fig. 1 illustrates a running state of internal-combustion engine 10, is positioned at one at these state power plant 11 to be preferably power plant 85% load operation at full capacity more than the power plant loads higher extreme value.In this case, as shown in Figure 1, power plant fuel tank 18 is connected by first hydraulic press 15 that oil pipe 19 and coupling are associated on the exhaust-gas turbocharger 13; Second hydraulic press 17 that first hydraulic press 15 and coupling is associated on the live axle 12 by oil pipe 20 is connected; Second hydraulic press 17 is in power plant fuel tank 18 by oil pipe 21 and is connected.First hydraulic press 15 with exhaust-gas turbocharger 13 couplings connection moves in the generator duty in this case, wherein the mechanical excess power of exhaust-gas turbocharger 13 converts hydraulic power to by first hydraulic press 15, and this hydraulic power is converted to mechanical output and joined live axle 12 the insides by second hydraulic press 17 in the dynamically working system of same hydraulic press.Therefore being positioned at power plant load higher extreme value at the power plant load makes the mechanical excess power of exhaust-gas turbocharger 13 convert the driving power of live axle 12 to by means of two hydraulic presses 15 and 17 when above.Two hydraulic presses 15 and 17 by oil pipe 19,20 with 21 mutually the mutual coupling connection and with the power plant fuel tank 18 couplings connection of power plant oil return line.
If being positioned at power plant load low extreme value with one, power plant are preferably power plant 25% load operation at full capacity, then join by second hydraulic press, 17 couplings that an oil pipe 22 and coupling are associated on the live axle 12 according to Fig. 2 power plant fuel tank 18, second hydraulic press 17 is connected by first hydraulic press 15 that oil pipe and coupling are associated on the exhaust-gas turbocharger 13, and first hydraulic press 15 is in the power plant fuel tank by oil pipe 24 again and is connected.Second hydraulic press 17 with live axle 12 couplings connection moves in a generator duty in this case, is used for taking out mechanical output and converting hydraulic power to from live axle.Then this hydraulic power is converted to mechanical output and joined exhaust-gas turbocharger 13 the insides by first hydraulic press 15 with exhaust-gas turbocharger 13 couplings connection.Therefore two hydraulic presses 15 of this running state and 17 also with the oil pipe coupling connection of power plant oil return line.
Hydraulic press 15 and 17 is made of the hydraulic press with constant displacement volume in the embodiment of Fig. 1 and 2.Flow by hydraulic press 15 and 17 can be regulated by adjustable back pressure regulator 25 and 26.In the running state of Fig. 1, be positioned at power plant load operation more than the power plant loads higher extreme value with one at these state power plant 11, effectively and modulating valve 26 is invalid at this state back pressure regulator 25.And, be positioned at power plant load operation below the power plant load low extreme value with one at this state in the running state of Fig. 2, at this state back pressure regulator 26 effectively and modulating valve 25 is invalid.Two back pressure regulators 25 and 26 are prepended to two hydraulic presses 15 and 17. respectively and represent the through-flow direction of oil by oil pipe 19 to 21 and 22 to 24 by the arrow in the oil pipe in Fig. 1 and 2 on the through-flow direction of oil.
Therefore for according to two hydraulic presses of internal-combustion engine of the present invention not only be positioned at the running state more than the power plant load higher extreme value and also be positioned at below the power plant load low extreme value running state all with the oil pipe of power plant oil return line mutual coupling connection mutually.Therefore the oil pipe that relates to the original power plant oil return line that just exists on meaning of the present invention can not add one of the genuine realization internal-combustion engine of hydraulic tube very compact structure form.Described internal-combustion engine is because compact structure form and few power-weight ratio and unusual.
Fig. 3 and 4 illustrates another embodiment according to internal-combustion engine 27 of the present invention, wherein correspond essentially to internal-combustion engine 10, therefore use identical label symbol for identical structure member for fear of unnecessary repetition according to the embodiment of Fig. 1 and 2 according to the embodiment's of Fig. 3 and 4 internal-combustion engine 27.Fig. 3 illustrates internal-combustion engine 27 in the running state more than the power plant loads higher extreme value and Fig. 4 is illustrated in the running state below the power plant load low extreme value.Only describe the difference of internal-combustion engine 27 with the internal-combustion engine 10 of Fig. 1 and 2 of Fig. 3 and 4 below in detail.
Constitute by hydraulic press at hydraulic press 15 described in the embodiment of Fig. 3 and 4 and 17, therefore can save the back pressure regulator of independent formation with adjustable permutation volume.Can directly regulate for this hydraulic press volume flow by volume flow with adjustable permutation volume.When using this hydraulic press with adjustable permutation volume, can further reduce the structure shape and the structure weight of internal-combustion engine.
List of numerals
10 internal combustion engines
11 power set
12 driving shafts
13 exhaust-driven turbo-charger exhaust-gas turbo chargers
14 clutches
15 first hydraulic presses
16 clutches
17 second hydraulic presses
18 power plant fuel tanks
19 oil pipes
20 oil pipes
21 oil pipes
22 oil pipes
23 oil pipes
24 oil pipes
25 back pressure regulators
26 back pressure regulators
27 internal-combustion engines
Claims (5)
1. internal-combustion engine, have power plant (11), this power plant combustion fuel and join a live axle (12) the inside of power plant (11) by the power that combustion fuel produces, this internal-combustion engine also has an exhaust-gas turbocharger (13), it reduces pressure the exhaust flow that leaves motor of the internal-combustion engine (11) in a turbo machine, and to make thus obtained power be to be used for compressing the combustion air flow that will be transported to power plant to join compressor the inside, one of them is by a turbine rotor and an exhaust-gas turbocharger rotor and one first hydraulic press (15) the coupling connection that compressor drum constitutes of exhaust-gas turbocharger (13), wherein the live axle (12) of power plant (11) also joins with second hydraulic press (17) coupling, and:
A) work as power plant, during (11) with a load operation that is positioned at more than the power plant load higher extreme value, should by with first hydraulic press of exhaust-gas turbocharger rotor coupling connection, (15) in a generator duty of same hydraulic press, from the exhaust-gas turbocharger rotor, take out mechanical work and convert the hydraulic pressure merit to, then with this hydraulic pressure merit by with second hydraulic press of live axle coupling connection, (17) in a dynamically working system of same hydraulic press, convert mechanical work to and join live axle, (12) the inside
B) work as power plant, during (11) with a load operation that is positioned at below the power plant load low extreme value, should by with the live axle of power plant, (12) second hydraulic press of coupling connection, (17) in a generator duty of same hydraulic press, from live axle, take out mechanical work and convert the hydraulic pressure merit to, then with this hydraulic pressure merit by with first hydraulic press of exhaust-gas turbocharger rotor coupling connection, (15) in a dynamically working system of same hydraulic press, convert mechanical work to and join exhaust-gas turbocharger, (13) the inside
C) with first hydraulic press (15) of exhaust-gas turbocharger rotor coupling connection with under the centre is connected the condition of a power plant fuel tank (18), pass through the oil pipe (19 of a power plant oil return line respectively with second hydraulic press (17) of live axle coupling connection, 20,21,22,23,24) coupling connection.
2. internal-combustion engine as claimed in claim 1 is characterized in that, described power plant load higher extreme value is about power plant fully loaded 85%.
3. internal-combustion engine as claimed in claim 1 or 2 is characterized in that, described power plant load low extreme value is about power plant fully loaded 25%.
4. as each or several described internal-combustion engines in the claim 1 to 3, it is characterized in that described first hydraulic press (15) and second hydraulic press (17) are made of the hydraulic press with adjustable permutation volume.
5. as each or several described internal-combustion engines in the claim 1 to 3, it is characterized in that, described first hydraulic press (15) and second hydraulic press (17) are made of the hydraulic press with constant displacement volume, wherein to each hydraulic press (15,17) a difference preposition back pressure regulator (25,26).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102005026602.9 | 2005-06-09 | ||
| DE102005026602A DE102005026602B3 (en) | 2005-06-09 | 2005-06-09 | Internal combustion engine, e.g. for motor vehicle, has exhaust gas supercharger connected to first hydraulic machine and engine drive shaft to second hydraulic machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1877099A true CN1877099A (en) | 2006-12-13 |
| CN100585142C CN100585142C (en) | 2010-01-27 |
Family
ID=36651388
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200610094553A Expired - Fee Related CN100585142C (en) | 2005-06-09 | 2006-06-09 | Internal combustion engine |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JP4758828B2 (en) |
| KR (1) | KR20060128666A (en) |
| CN (1) | CN100585142C (en) |
| DE (1) | DE102005026602B3 (en) |
| FI (1) | FI124489B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102400774A (en) * | 2011-11-11 | 2012-04-04 | 中国重汽集团济南动力有限公司 | Sinotruk D12-series engine |
| CN103850781A (en) * | 2014-03-28 | 2014-06-11 | 长城汽车股份有限公司 | Supercharger |
| CN108506094A (en) * | 2017-02-28 | 2018-09-07 | 日立汽车系统(苏州）有限公司 | Gas-turbine unit |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3532938C1 (en) * | 1985-09-14 | 1986-09-18 | M.A.N.-B & W Diesel GmbH, 8900 Augsburg | Internal combustion engine charged by means of an exhaust gas turbocharger with an exhaust gas excess energy conversion device |
| DE3703143A1 (en) * | 1987-02-03 | 1988-08-11 | Thomson Brandt Gmbh | METHOD FOR TRANSMITTING AN AUDIO SIGNAL |
-
2005
- 2005-06-09 DE DE102005026602A patent/DE102005026602B3/en not_active Expired - Fee Related
-
2006
- 2006-06-02 JP JP2006155061A patent/JP4758828B2/en not_active Expired - Fee Related
- 2006-06-05 KR KR1020060050334A patent/KR20060128666A/en active Search and Examination
- 2006-06-07 FI FI20060559A patent/FI124489B/en not_active IP Right Cessation
- 2006-06-09 CN CN200610094553A patent/CN100585142C/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102400774A (en) * | 2011-11-11 | 2012-04-04 | 中国重汽集团济南动力有限公司 | Sinotruk D12-series engine |
| CN103850781A (en) * | 2014-03-28 | 2014-06-11 | 长城汽车股份有限公司 | Supercharger |
| CN103850781B (en) * | 2014-03-28 | 2016-04-13 | 长城汽车股份有限公司 | Pressurized machine |
| CN108506094A (en) * | 2017-02-28 | 2018-09-07 | 日立汽车系统(苏州）有限公司 | Gas-turbine unit |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4758828B2 (en) | 2011-08-31 |
| FI20060559A (en) | 2006-12-10 |
| FI124489B (en) | 2014-09-30 |
| FI20060559A0 (en) | 2006-06-07 |
| DE102005026602B3 (en) | 2006-11-30 |
| JP2006342801A (en) | 2006-12-21 |
| CN100585142C (en) | 2010-01-27 |
| KR20060128666A (en) | 2006-12-14 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CP01 | Change in the name or title of a patent holder | ||
| CP01 | Change in the name or title of a patent holder |
Address after: Augsburg Patentee after: MAN ENERGY SOLUTIONS SE Address before: Augsburg Patentee before: Man Diesel & Turbo SE |
|
| CP03 | Change of name, title or address | ||
| CP03 | Change of name, title or address |
Address after: Augsburg Patentee after: MAN DIESEL SE Address before: Osborg, Germany Patentee before: Man B&W Diesel AG |
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| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20190506 Address after: Augsburg Patentee after: Man Diesel & Turbo SE Address before: Augsburg Patentee before: Man Diesel Se |
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| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20100127 Termination date: 20210609 |