CN1252854A - Fuel injection pump for IC engines, in particular big, slow marine diesel engines - Google Patents
Fuel injection pump for IC engines, in particular big, slow marine diesel engines Download PDFInfo
- Publication number
- CN1252854A CN1252854A CN98804357A CN98804357A CN1252854A CN 1252854 A CN1252854 A CN 1252854A CN 98804357 A CN98804357 A CN 98804357A CN 98804357 A CN98804357 A CN 98804357A CN 1252854 A CN1252854 A CN 1252854A
- Authority
- CN
- China
- Prior art keywords
- plunger
- hole
- pump
- edge
- fuel oil
- 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
- 239000000446 fuel Substances 0.000 title claims abstract description 22
- 238000002347 injection Methods 0.000 title abstract description 8
- 239000007924 injection Substances 0.000 title abstract description 8
- 238000002485 combustion reaction Methods 0.000 claims abstract description 4
- 239000000295 fuel oil Substances 0.000 claims description 27
- 230000003068 static effect Effects 0.000 claims description 4
- 239000003921 oil Substances 0.000 claims description 2
- 230000003628 erosive effect Effects 0.000 abstract description 5
- 230000010355 oscillation Effects 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 4
- 230000003139 buffering effect Effects 0.000 description 2
- 230000006837 decompression Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 239000007921 spray Substances 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000000567 combustion gas Substances 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
Images
Classifications
-
- 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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
-
- 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
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
- F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
- F02M59/265—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders characterised by the arrangement or form of spill port of spill contour on the piston
Abstract
A fuel injection pump for internal combustion engines, in particular big, slow marine diesel engines, for supply of a variable amount of fuel to an injection nozzle positioned in the working cylinder of the engine, said injection nozzle having a spring-loaded needle in the nozzle aperture, and which pump comprises a barrel (2), in which a plunger (3) with an upper edge (4) formed between the end surface and the side surface of the plunger and at least one helically extending oblique cut-off edge (6), is movable, which oblique cut-off edge (6) defines a recess (5) in the side surface of the plunger, which recess is connected through an axial duct (9) with the end surface of the plunger, and in which the wall of the barrel (2) has at least one cut-off hole (11), which opens into a surrounding supply chamber containing the fuel under moderate pressure, said at least one hole at the travel of the plunger from the bottom to the top position being covered by the side surface of the plunger below the upper edge and being later uncovered by the oblique cut-off edge for diversion of excess fuel at the end of the effective pump stroke. To overcome problems due to erosion and pressure oscillation in pumps of big dimensions, the pumps are designed such that at least one of the cut-off holes (11) contains a flow limiting means (13) placed at a distance from the wall of the barrel, said means defining a chamber (20) positioned between the cylindrical wall of the barrel (2) and the flow-limiting means.
Description
The present invention relates to the fuel oil injectionpump that internal-combustion engine is specially big, slow marine diesel, this pump is used for carrying to the nozzle that is positioned at the engine operation cylinder fuel oil of variable quantity, said nozzle has spring-loaded eedle in its spray orifice, said pump comprises cylinder barrel, plunger can move in cylinder barrel, this plunger has the inclination of the top edge that forms and at least one spiral extension by the edge between its end surfaces and side surface, this tilts and forms a recess by the edge on the side surface of plunger, this recess is connected in the end surfaces of plunger by axial pipe, and the cylinder barrel wall has at least one by the hole in this cylinder barrel, the fuel feeding chamber on every side that comprises the medium pressure fuel oil is led in this hole, above-mentioned at least one hole is positioned on the stroke of plunger from the bottom position to the tip position, the plunger side surface of this hole below top edge covers, and subsequently at the end of actual pump stroke by coming out, so that shift superfluous fuel oil by the edge.
In conventional fuel oil injectionpump, it is right that each inclination is made into by edge and the hole of passing the cylinder barrel wall, and plunger is designed such that this hole is covered by the top edge of plunger when plunger stroke begins, and just expose by the edge by tilting when the fuel oil of established amount has been transported to nozzle subsequently in same hole.This be configured in work in the small-sized and medium duty engine satisfactory, but problem just takes place, the measure that must take for the variation in pressure that suppresses in the ejecting system when the actual plunger stroke that this problem can be traced to the large scale of pump and pump begins and finishes in the big, slow diesel engine.This problem is the cavitation erosion of plunger side surface, and this originates from high flow rate very and the cavitation that causes.But can not increase the cross section in hole immediately, because the hole is being scheduled to when the edge exposes postpone the pressure reduction by the certain flow resistance of effect by tilting to end.This delay is essential, to prevent to cause cavitation and prevent that combustion gas enters nozzle in nozzle.When using the fuel oil of poor lubricity, if possible, also wish in the upper edge region of plunger, between plunger and cylinder barrel, to obtain sizable supporting surface, with the danger that reduces to block in this zone.
A kind of fuel oil injectionpump is disclosed in German Offenlegungsschrift No.25 32 205, in this pump, plunger covers the vent of cylinder barrel when tip position moves from bottom position, and expose this vent subsequently, so that unnecessary fuel is transferred in the annular space that surrounds pump cylinders, and some throttle orifice parts are housed, the reflow pipe that comes out from annular space to reduce the danger of cavitation.
Above-mentioned prior art is said to be not too effective in patent US-A-5015160, discloses a kind of device in this patent.This kind device is being paid special attention to during covering vent at the pressure that form 50 crust in the annular space of cylinder barrel, utilizes one-way valve in sucking pipe and the spring-loaded pressure valve in the reflow pipe to keep this pressure.This device is very complicated because many parts are arranged, and keeps also very difficult.
The purpose of this invention is to provide a kind of fuel-injection pump, utilize this pump and can prevent effectively that by the better way device zone near the plunger top edge from cavitating.
The feature of utilization disclosed fuel oil injectionpump in the feature clause of claim 1 can satisfy this purpose of the present invention.
In fuel oil injectionpump of the present invention, current-limiting apparatus is contained in ending in the hole of cylinder barrel wall.Like this, space between plunger and current-limiting apparatus just forms the pressure of remarkable increase, this current-limiting apparatus is throttle orifice parts, and above-mentioned pressure can prevent to produce cavitation near the zone of plunger top edge effectively, and no matter how high the flow velocity of instantaneous generation have.Even reduce elevated pressure by the throttle orifice parts, also produce sizable flow velocity at these throttle orifice parts, but the measure of being taked is quite simple with respect to prior art, and proved effective, no matter be to reduce cavitation itself, still it is transferred to other zone that does not produce cavitation erosion fully.
The fuel pump that the present invention is specially adapted to the beginning of actual pump stroke and finishes to be controlled by the hole group of separating.According to the present invention, the throttle orifice component configuration is at the Kong Zuzhong of beginning pump stroke.
According to the present invention, the throttle orifice parts have a kind of like this bore, make the static pressure in the hole in the place ahead, top reach pump discharge pressure 10～20%.Be surprised to find that the formation of pressure before the fuel oil that strong throttling discharges can influence sharply and spray.
Describe the present invention with reference to the accompanying drawings in detail, these figure are:
Fig. 1 is the axial, cross-sectional view of fuel oil injectionpump of the present invention;
Fig. 2 is the cross-sectional view that passes through the intercepting of cylinder barrel wall along the II-II line of Fig. 1;
Fig. 3 is a plotted curve, is illustrated in the pressure in the pump of the present invention during the fuel injection,
Fig. 4 a, 4b and 4c schematically illustrate the longitdinal cross-section diagram by the hole.
Fig. 1 illustrates the longitdinal cross-section diagram of fuel oil injectionpump 1, and this pump comprises the cylinder barrel 2 that plunger 3 can move therein.Cylinder barrel 2 is suitable for being contained in the pump seat of conventional design, and this pump seat comprises the fuel feeding chamber around the cylinder barrel intermediate portion, and excessive fuel oil can be transferred in this pump seat, and fuel oil can be transported in the cylinder barrel from pump seat during the return stroke of plunger.Plunger 3 is included in the top edge 4 that forms between the end of plunger and the side surface.Plunger also comprises recess 5, and this recess is formed by edge 6 by the inclination towards the plunger end surface direction, and this edge is along the side surface spiral extension of plunger.Tilt and extend for example hexagonal angle by edge 6, plunger has the edge that ends of two relative configurations usually.Plunger 3 is equipped with the connection set 7 and 8 as rotating mechanism, utilizes this device 7, can rotary plunger, thus regulate fuel delivery, and plunger is moved axially as the connection set 8 of roller guide.These mechanisms are not parts of the present invention, can adopt conventional design.Plunger 3 also comprises axial pipe 9, and this conduit can make the space 10 above recess 5 and the plunger end surface 4 be communicated with.
This pump is suitable for the fuel delivery of the Variable quantity nozzle in the diesel engine work cylinder.Rotary plunger 3 just can be regulated quantity delivered.When the edge on plunger end surface 4 covers a batch total on the pump cylinders 2 during it moves upward and by hole 11, begin actual pump stroke thus, when tilting when edge 6 exposes one group of vent 12, actual stroke finishes, thereby the pressure in the pump chamber above the plunger end surface 4 is by axial pipe 9, recess 5 with lead to reducing pressure by hole 12 around the fuel feeding chamber of cylinder barrel 2.
At the big, slow diesel engine for example in the fuel oil syringe pump of marine diesel engine, produce special problem owing to the size of pump pressure big and injected fuel is high, utilize described pump, using specially designed timing hole and vent separately when actual pump stroke begins and finishes can head it off.Owing to adopt group hole separately, the timing hole can be designed to prevent from effectively to originate from the unexpected cavitation that fuel oil stream is caused of interrupting spraying at a high speed, and vent can be designed to be suitable for suitably making the oil decompression that is transferred, cause gasoline in the cylinder to infiltrate the danger of nozzle until overcoming, or be designed to prevent from nozzle, to take place cavitation.In addition, the axially spaced-apart of suitably choosing between hole 11 and 12 can make the top of plunger and the bearing surface between the cylinder barrel wall have suitable dimensions.
The cross section in timing hole is usually designed to the cross section greater than vent 12.Yet according to the present invention, throttle orifice parts 13 are configured in the timing hole to the outlet of fuel feeding chamber, as shown in Figure 2, can prevent cavitation most effectively.The throttle orifice parts form a kind of like this runner, make pressure in the throttle orifice in throttle orifice parts the place ahead at the edge 4 on plunger end surface 4 through out-of-date, to be ready covering and before the hole, significantly to surpass the indoor pressure of fuel feeding.The pressure that causes postponing on the plunger side surface in the flow resistance that causes on the throttle orifice parts reduces, thereby cavitation does not take place.
The vent that exposes by edge 6 by tilting is usually designed to has the vertical section that is the diffuser shape, has minimum cross section on the cylinder barrel wall.Requirement has little cross section on the cylinder barrel wall, so that expose hole 12 soon, thereby obtain the good pressure reduction curve of shape in ejecting system.
The plotted curve of Fig. 3 illustrates the pressure diagram as the fuel oil injectionpump of the present invention of crank shaft angle function.The entire curve of drawing is represented the pressure in the pump chamber 10.This curve shows that the pressure in pump chamber when plunger 3 moves upward begins to increase, but just begins rapid rising at point 14, and at this point, the plunger of timing hole 11 below top edge 4 covers.Open at point 15 nozzles, and when continuing throw of pump, the fuel injection of established amount is in the working cylinder of motor.At point 16, expose by hole 16, subsequently, the pressure in the pump chamber reduces with the process of buffering, has so just reduced the pressure surge in the ejecting system, thereby has guaranteed the correct closing operation of eedle in the nozzle.Dotted line 17 is illustrated in the pressure diagram in the chamber between throttle part and the plunger side, has the throttle orifice parts 13 of appropriate size in this chamber.Can see that pressure reduces gradually, above-mentioned pressure reduces the cavitation that can prevent effectively in the above-mentioned hole of plunger side.
The fuel oil injectionpump that the invention is not restricted to timing hole on the pump cylinders and separate by the hole, but also can be successfully used to tilt by the identical fuel oil injectionpump of number of edges by number of perforations and plunger, promptly wherein utilize hole identical on the cylinder barrel wall to begin the jet pump of operating with end injection.In the design of this pump, current-limiting apparatus both had been configured for preventing cavitation and the device that prevents relevant plunger cavitation erosion, was configured for the device that basic controlling pressure descends when actual pump stroke finishes again.
Fig. 4 a, 4b and 4c schematically illustrate the embodiment by the hole who sees in the longitudinal cross-section.Fig. 4 a illustrates an embodiment, and in this embodiment, the current-limiting apparatus that forms throttle orifice parts 21 is configured in hole 20, near the outlet 22 that enters the fuel feeding chamber.In this embodiment, by by and the size maximum in the chamber of unloading and supercharging, thereby the chamber between throttle orifice parts and inlet reaches the maximum possible volume, thereby can keep-up pressure as well as possiblely.Throttle part can be designed to have some conduits, or the flow direction that is designed to make conduit is with by the axis in hole at an angle.With the advantage by axially bored line conduit at an angle is that the fluid out of plumb ground that reduces pressure contacts with the wall of relative fuel feeding chamber, thereby has reduced the danger of the above-mentioned wall that cavitates.In addition, the chamber between cylinder barrel wall and the throttle orifice parts can be the non-cylindrical shape.Its shape can be for example taper, makes to be slightly smaller than the diameter in chamber by aperture on the cylinder barrel wall, can insert the throttle orifice parts in this cone shape hole.Like this, the fluid control action can be divided hole and the throttle orifice parts of tasking on the cylinder barrel wall, the timing that if there is no separates and by the hole, and this is favourable.
Fig. 4 c illustrates the preferred embodiment by hole 20 that the throttle orifice parts are housed.These throttle orifice parts 24 general arrangements should be designed to diffuser 25 in the direction facing to fuel feeding chamber outlet 22 by the hole by the middle part in hole.The purpose of diffuser 25 is the speed that reduces to leave the jet flow of throttle part.By suitably choosing the size of throttle orifice parts 21,23 or 24, when covering by the hole, can when ending, form pressure in the place ahead at the throttle orifice parts, make cavitation be eliminated, and can carry out buffering type decompression, make pressure reduce and significant pressure surge does not take place.If desired, can suitably design the axial pipe in the plunger, to constitute other buffer function.
Claims (3)
1. an internal-combustion engine is specially the fuel oil injectionpump of big, slow marine diesel, this pump is used for the fuel oil of the nozzle conveying Variable quantity in being contained in the engine operation cylinder, said nozzle has spring-loaded eedle in spray-hole, this pump comprises cylinder barrel, plunger can move in this cylinder barrel, this plunger has the inclination of the top edge that forms and at least one spiral extension by the edge between plunger end surface and side surface, this tilts and constitutes a recess by the edge on the side surface of plunger, this recess is communicated with the end surfaces of plunger by axial pipe, and on the cylinder barrel wall of this pump, has at least one by the hole, it is indoor to lead to the periphery fuel feeding that comprises the medium pressure fuel oil by the hole, above-mentioned at least one by the hole side surface below plunger top edge covering when plunger move from the bottom position to the tip position, and when finishing, exposes by the edge actual pump stroke subsequently by tilting, so that shift excessive fuel oil, and in the hole, providing a kind of device, so that in that at least one forms the static pressure that increases in the hole at this during a part of stroke of plunger, this pump is characterised in that, this device that is used to increase static pressure is the throttle orifice parts, these throttle orifice parts are contained in the hole, its aperture is reduced to such degree with respect to the cross section by the hole, makes by producing elevated pressure in ending in the hole of throttle orifice parts the place ahead between preceding and expiration date.
2. fuel oil injectionpump as claimed in claim 1, in this pump, the beginning of actual pump stroke and end be is characterized in that by some groups of holes controls that separate the throttle orifice component configuration is in that group hole of beginning pump stroke.
3. fuel oil injectionpump as claimed in claim 2 is characterized in that the throttle orifice parts have such bore, make by the time static pressure reach pump charge oil pressure 10～20%.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DK0443/97 | 1997-04-21 | ||
| DK199700443A DK176162B1 (en) | 1997-04-21 | 1997-04-21 | Fuel pump for internal combustion engines, especially large slow-moving marine diesel engines |
| DK0443/1997 | 1997-04-21 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1252854A true CN1252854A (en) | 2000-05-10 |
| CN1081740C CN1081740C (en) | 2002-03-27 |
Family
ID=8093601
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN988043572A Expired - Fee Related CN1081740C (en) | 1997-04-21 | 1998-04-08 | Fuel injection pump for IC engines, in particular big, slow marine diesel engines |
Country Status (9)
| Country | Link |
|---|---|
| EP (1) | EP0977944B1 (en) |
| JP (1) | JP3588365B2 (en) |
| KR (1) | KR100440828B1 (en) |
| CN (1) | CN1081740C (en) |
| AU (1) | AU7030298A (en) |
| DE (1) | DE69805999T2 (en) |
| DK (1) | DK176162B1 (en) |
| IT (1) | IT1299426B1 (en) |
| WO (1) | WO1998048166A1 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100443715C (en) * | 2004-03-05 | 2008-12-17 | 博世株式会社 | Fuel injection pump for internal combustion engine |
| CN100487234C (en) * | 2002-11-21 | 2009-05-13 | 洋马株式会社 | Fuel injection pump |
| CN110312861A (en) * | 2017-02-14 | 2019-10-08 | 罗伯特·博世有限公司 | The low tension loop of restricting element and the fuel injection system with restricting element |
| CN111480000A (en) * | 2017-12-26 | 2020-07-31 | 日立汽车系统株式会社 | Fuel supply pump |
| CN112096551A (en) * | 2019-06-17 | 2020-12-18 | 曼恩能源方案有限公司 | Fuel pump |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE112005003302B4 (en) * | 2004-12-27 | 2024-01-04 | Hyundai Heavy Industries Co. Ltd. | Fuel injection pump with a structure that prevents cavitation damage |
| KR100895948B1 (en) | 2004-12-27 | 2009-05-07 | 현대중공업 주식회사 | Fuel injection pump to prevent cavitation erosion |
| KR100992227B1 (en) | 2008-10-27 | 2010-11-05 | 현대중공업 주식회사 | Prevention device of cavitation erosion damage in the fuel injection pump of the diesel engine |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1271799A (en) * | 1968-09-24 | 1972-04-26 | Cav Ltd | Fuel injection pumps |
| US4118156A (en) * | 1976-12-01 | 1978-10-03 | Sulzer Brothers Limited | Fuel injection pump having choke means in overflow line |
| DE3820706A1 (en) * | 1988-06-18 | 1989-12-21 | Bosch Gmbh Robert | INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES |
| DE3820707A1 (en) * | 1988-06-18 | 1989-12-21 | Bosch Gmbh Robert | INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES |
-
1997
- 1997-04-21 DK DK199700443A patent/DK176162B1/en not_active IP Right Cessation
-
1998
- 1998-04-08 KR KR10-1999-7009694A patent/KR100440828B1/en not_active IP Right Cessation
- 1998-04-08 CN CN988043572A patent/CN1081740C/en not_active Expired - Fee Related
- 1998-04-08 EP EP98916865A patent/EP0977944B1/en not_active Expired - Lifetime
- 1998-04-08 WO PCT/DK1998/000149 patent/WO1998048166A1/en active IP Right Grant
- 1998-04-08 JP JP54475598A patent/JP3588365B2/en not_active Expired - Fee Related
- 1998-04-08 AU AU70302/98A patent/AU7030298A/en not_active Abandoned
- 1998-04-08 DE DE69805999T patent/DE69805999T2/en not_active Expired - Lifetime
- 1998-04-20 IT IT98RM000248A patent/IT1299426B1/en active IP Right Grant
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100487234C (en) * | 2002-11-21 | 2009-05-13 | 洋马株式会社 | Fuel injection pump |
| CN100443715C (en) * | 2004-03-05 | 2008-12-17 | 博世株式会社 | Fuel injection pump for internal combustion engine |
| CN110312861A (en) * | 2017-02-14 | 2019-10-08 | 罗伯特·博世有限公司 | The low tension loop of restricting element and the fuel injection system with restricting element |
| CN110312861B (en) * | 2017-02-14 | 2021-08-31 | 罗伯特·博世有限公司 | Throttle element and low-pressure circuit of a fuel injection system having a throttle element |
| CN111480000A (en) * | 2017-12-26 | 2020-07-31 | 日立汽车系统株式会社 | Fuel supply pump |
| CN111480000B (en) * | 2017-12-26 | 2021-12-10 | 日立安斯泰莫株式会社 | Fuel supply pump |
| CN112096551A (en) * | 2019-06-17 | 2020-12-18 | 曼恩能源方案有限公司 | Fuel pump |
| CN112096551B (en) * | 2019-06-17 | 2023-10-13 | 曼恩能源方案有限公司 | fuel pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2001520719A (en) | 2001-10-30 |
| EP0977944A1 (en) | 2000-02-09 |
| KR20010020139A (en) | 2001-03-15 |
| WO1998048166A1 (en) | 1998-10-29 |
| EP0977944B1 (en) | 2002-06-12 |
| IT1299426B1 (en) | 2000-03-16 |
| DE69805999T2 (en) | 2002-11-28 |
| AU7030298A (en) | 1998-11-13 |
| DE69805999D1 (en) | 2002-07-18 |
| ITRM980248A0 (en) | 1998-04-20 |
| DK44397A (en) | 1998-10-22 |
| CN1081740C (en) | 2002-03-27 |
| JP3588365B2 (en) | 2004-11-10 |
| KR100440828B1 (en) | 2004-07-19 |
| ITRM980248A1 (en) | 1999-10-20 |
| DK176162B1 (en) | 2006-10-23 |
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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 | ||
| C56 | Change in the name or address of the patentee |
Owner name: MAN DIESEL AS Free format text: FORMER NAME: MAN DIESEL AS Owner name: MAN DIESEL ENGINES AND TURBINE GERMAN SUBSIDIARY, Free format text: FORMER NAME: MAN DIESEL AS Owner name: MAN DIESEL AS Free format text: FORMER NAME: MAN B + W DIESEL AS. |
|
| CP01 | Change in the name or title of a patent holder |
Address after: Copenhagen Patentee after: MAN DIESEL & TURBO FILIAL AF MAN DIESEL & TURBO SE TYSKLAND Address before: Copenhagen Patentee before: MAN DIESEL & TURBO FILIAL AF MAN DIESEL & TURBO SE TYSKLAND Address after: Copenhagen Patentee after: MAN DIESEL & TURBO FILIAL AF MAN DIESEL & TURBO SE TYSKLAND Address before: Copenhagen Patentee before: MAN DIESEL filial af MAN Diesel SE Tyskland Address after: Copenhagen Patentee after: MAN DIESEL filial af MAN Diesel SE Tyskland Address before: Copenhagen Patentee before: MAN B & W DIESEL A/S |
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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: 20020327 Termination date: 20170408 |