CN1223772C - Internal combustion engine for driving propeller shaft - Google Patents
Internal combustion engine for driving propeller shaft Download PDFInfo
- Publication number
- CN1223772C CN1223772C CNB021071284A CN02107128A CN1223772C CN 1223772 C CN1223772 C CN 1223772C CN B021071284 A CNB021071284 A CN B021071284A CN 02107128 A CN02107128 A CN 02107128A CN 1223772 C CN1223772 C CN 1223772C
- Authority
- CN
- China
- Prior art keywords
- thrust
- combustion engine
- internal
- bearing
- propelling cam
- 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.)
- Expired - Fee Related
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H21/00—Use of propulsion power plant or units on vessels
- B63H21/12—Use of propulsion power plant or units on vessels the vessels being motor-driven
- B63H21/14—Use of propulsion power plant or units on vessels the vessels being motor-driven relating to internal-combustion engines
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H21/00—Use of propulsion power plant or units on vessels
- B63H21/30—Mounting of propulsion plant or unit, e.g. for anti-vibration purposes
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- 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
- F02B61/00—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing
- F02B61/04—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing for driving propellers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/22—Internal combustion engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/31—Axle
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Ocean & Marine Engineering (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Sliding-Contact Bearings (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
An internal combustion engine for driving a propeller shaft is composed of a rearmost main bearing of the internal combustion engine arranged between the throw of a crankshaft and a thrust cam inside a thrust bearing. A thrust segment(20) is arranged between a forward facing sliding face(22) on the thrust cam and a rearward facing supporting face(18) on a fixed type main bearing housing. Within a circumferential area, the thrust cam has a rotationally symmetric arc shaped recessed part(28) extending radially inward to the position of a height without exceeding an intermediate portion of the thrust segment (20).
Description
Technical field
The present invention relates to a kind of internal-combustion engine that is used to drive screw shaft, main bearing place in its rear-most end, it has a thrust-bearing, on the axial direction of bent axle, described main bearing is positioned between the footstalk of a bent axle and the propelling cam of described thrust-bearing (thrust cam), this propelling cam can rotate with described bent axle, thrust bearing shoe be arranged on propelling cam axially forward slip surface and the internal-combustion engine base plate described between axially backward the supporting surface of stationary axle bearing of main bearing.
Background technique
In internal-combustion engine, a such thrust-bearing is integrated in the base plate of main bearing of engine rear-most end, can motor is shortened.This internal-combustion engine generally is the master motor of large ship.Described large ship is such as being Container ship.In this internal-combustion engine, very large moment of torsion must be passed to propeller cavitation from motor by screw shaft.When propeller cavitation promotion boats and ships advanced, propeller cavitation was given power forward of screw shaft, and this power passes to engine foundation by described base plate in described thrust-bearing.
Power transmission from the running shaft to the base plate is undertaken by thrust bearing shoe, and thrust bearing shoe is static with respect to the supporting surface of main bearing seat basically.Slip surface on the propelling cam slides on the supporting surface of thrust bearing shoe, and lubricant film is maintained between this supporting surface and the described slip surface by means of the lubrication system of thrust-bearing.
Each thrust bearing shoe is adjusted with respect to described propelling cam separately, the total load ability of thrust-bearing be each thrust bearing shoe load carrying capacity and.Therefore, the load carrying capacity of wishing described thrust bearing shoe reasonably evenly distributes when work, may be the comparison difficulty in this thrust-bearing in being integrated in main bearing, because in the fan-shaped part that make progress relative, do not have thrust bearing shoe with dismountable top of main bearing.Therefore, the part that makes progress of current propelling cam is not subjected to the supporting of thrust bearing shoe in the axial direction.
Summary of the invention
The objective of the invention is to improve the load carrying capacity of the thrust-bearing in the internal-combustion engine.
For this reason, the invention provides a kind of internal-combustion engine that is used to drive screw shaft, has a thrust-bearing at the main bearing place of its rear-most end, on the axial direction of bent axle, described main bearing is between the propelling cam of the footstalk of a bent axle and described thrust-bearing, this propelling cam can rotate with described bent axle, thrust bearing shoe be arranged on propelling cam axially forward slip surface and the internal-combustion engine base plate described between axially backward the supporting surface of stationary axle bearing of main bearing, it is characterized in that, described propelling cam has a rotational symmetric arc groove, and this groove radially inwardly extends to the neutral position of thrust bearing shoe at most.
In the oepration at full load that the load carrying capacity of thrust-bearing is utilized, the described arc groove in the described peripheral region means that in this peripheral region, propelling cam is not pressed to the radially outermost zone of thrust bearing shoe so massively.
At first, this means that thrust center (thrust centre) moves inward diametrically slightly.A transverse wall of the standing part of main bearing and described base plate forms an integral body, and this transverse wall is made by heavy material, and has rib shape stiffening rib.Therefore, the radially innermost zone adjacent with itself and axis hole in the main bearing compared, and the supporting surface rigidity in the zone that it is radially outermost is stronger.Under working load, the zone that the rigidity of supporting surface is stronger is out of shape smaller in the axial direction, and this causes on thrust bearing shoe, tends to have maximum load in its radially outermost zone.Arc groove in the described propelling cam has reduced the radially axial pressure in outermost zone of propelling cam, thereby the stronger rigidity of this area supporting face is compensated.
Secondly, never supported being converted to of described arc groove propelling cam on thrust-bearing provides a kind of more uniform pressure distribution in the supported zone.In the not supported zone of propelling cam, the peripheral region of propelling cam tends to deflection, and along with this peripheral region continues to rotate to supported zone, described deflection reduces, and makes the thrust bearing shoe that is positioned at the front be subjected to extra load.Described arc groove provides the part compensation to this overburdening, and this groove has reduced to act on the thrust loading on the bearing shell, and this is especially because the radially outermost zone that deflection took place of propelling cam is maximum.
If this groove is further extending radially inwardly, surpass the middle part of thrust bearing shoe, bearing shell can transmit the ground maximum thrust and just may reduce, and this is reluctant to see.
Best, described arc groove inwardly extends to 30% radially outermost place of thrust bearing shoe at most, because the radially innermost zone that influenced by maximum thrust just can comprise the big zone of of this thrust bearing shoe like this, this is favourable.
In a kind of preferred embodiment, described arc groove is positioned on the outer surface of propelling cam.It is bigger flexible that this groove makes propelling cam have in radially outermost zone.When the load on the thrust-bearing was low, the pressure on the propelling cam was just too low and can not make the propelling cam distortion, and described slip surface just can be arranged essentially parallel to described supporting surface.When the pressure on the propelling cam was high, because that this groove forms is bigger flexible, the radially outermost zone relative with this groove can be axially to this groove deflection.The thrust loading that described deflection means vast scale is more absorbed by the radially inner side zone of thrust axis watt.Therefore, to be slip surface regulate self shape by self according to the size of load to this embodiment's advantage, makes that to remain on lubricant film between thrust bearing shoe and this slip surface in good condition and have suitable thickness.
In one embodiment, described arc groove links to each other with at least one freezing mixture supplying pipe.By the normally freezing mixture of lubricant oil is provided to described arc groove, the front in the radially outermost zone of propelling cam and the back side obtain cooling simultaneously, thereby can keep lower temperature, thereby help to improve load carrying capacity, can not squeezed away because colder lubricant oil can transmit bigger thrust.Because freezing mixture is not to bring into play lubricating function in described arc groove, delivery rate can be adjusted according to the cooling needs fully.
In one embodiment, the propelling cam in the described internal-combustion engine has a radially outstanding flange, and sprocket wheel is fixed on a position that is positioned at the radial outside of described arc groove on this flange.In some cases, described thrust-bearing is arranged on the chain transmission equipment that drives the camshaft that is positioned at the motor rear end.In this case, flexible that arc groove obtains depend in the radially outermost zone that described sprocket wheel can the limit thrust cam.By described sprocket wheel is fixed on the described flange, this sprocket wheel only is fixed on the described propelling cam in a side of described arc groove, and that the opposite side of this groove has kept fully is required flexible.
In a kind of alternative design, described propelling cam has in the axial direction respectively at two barrel surfaces of arc groove both sides, and two ring parts of a sprocket wheel are respectively fixed on the described barrel surface.Two parts that described sprocket wheel are divided into the resilience (mutuallyflexible) of suitably helping each other have in the axial direction also prevented the flexible counteracting in the radially outermost zone of this sprocket wheel and propelling cam.
Perhaps, described arc groove can be arranged on the axial slip surface forward of propelling cam.But this can cause in the thrust-bearing of unloading, and than bigger in radially innermost zone, this can cause oil film very thick in the radially outermost zone of low-load to the distance between slip surface and the supporting surface in radially outermost zone.Yet this can't cause the problem moved.When thrust-bearing at full capacity, and radially outermost regional specific diameter gets more for a long time to innermost regional deflection, the distance between slip surface and the supporting surface will be more even, this even distribution on thrust bearing shoe that can promote to load improves load carrying capacity.
Because load upwards is more evenly distributed in the footpath of thrust bearing shoe, the present invention is very large, and Continuous Maximum Rating is at least in the two-stroke crosshead diesel engine of 40000kW and is particularly useful.Because generally will be under the slow-speed of revolution, 70 to 200rpm the rotating speeds very high power of output down for example, end thrust can be high, and thrust-bearing is corresponding to have very large-area thrust bearing shoe.Thereby the oil slick thickness between bearing shell and the slip surface is less with respect to the size of thrust bearing shoe, and, the skewness of thrust on bearing shell, this has remarkable influence to load carrying capacity.
Description of drawings
For a more detailed description below in conjunction with schematic representation to embodiments of the invention.In the accompanying drawing:
Fig. 1 is the side view of internal-combustion engine of the present invention;
Fig. 2 is the rear view of the thrust-bearing of internal-combustion engine shown in Figure 1;
Fig. 3 is the sectional view by the thrust-bearing among Fig. 2;
Fig. 4 and Fig. 5 are other embodiments of the present invention and the part corresponding section of Fig. 2;
Fig. 6 is by another embodiment's the propelling cam and the part section of thrust bearing shoe.
Embodiment
Fig. 1 illustrates an internal-combustion engine 1 that is connected to the screw shaft 3 that has propeller cavitation 4 by a jack shaft 2.This internal-combustion engine can be four stroke engine or two stroke engine, for example the applicant's ME type or MC type two-stroke cross head engine, and these motors are known for the person of ordinary skill of the art.Motor for example can have 30 to 120cm cylinder diameter, and the cylinder numerical example is as being 5 to 20, and for crosshead engine, rotating speed can be 60 to 300rpm.The output power of motor for example can be 3000 to 130000kW.Motor preferably has bigger output power, and such as 30000kW at least, the cylinder number is at least 8, and cylinder diameter is at least 70cm.
In the rear-most end main bearing 5 of bent axle 6, internal-combustion engine 1 has a thrust-bearing 7 in the rear view that is shown in Fig. 2, and the longitudinal section of this thrust-bearing is shown in Fig. 3.A transverse wall one casting of the fixed bearing block of main bearing 5 and motor base plate 8.This transverse wall is strengthened by bigger rib 9, to obtain big rigidity.This main bearing seat also comprises a dismountable top 10.This main bearing seat is coated with bearing metal on the internal surface of its formation axis hole, in described axis hole, be provided with an axle journal 12, footstalk arm in the bent axle footstalk of this main bearing seat and bent axle rear-most end links to each other, and forms integral body with propelling cam in the described thrust-bearing.At the rear side of propelling cam, extend in the axle journal 15 of same axial region in the bearing 16 that is bearing in rear-most end.This axle journal 15 ends at a flange 17, and the latter decides with the distance between motor rear end and the hull stern tube shaft pipe, perhaps is fixed on the jack shaft 2, perhaps directly is fixed on the screw shaft 3.
Rear side at fixing main bearing seat has a bottom around main bearing to extend to supporting surface ringwise, with the vertical center line 19 rectangular vertical basically planes of main bearing in.In illustrated embodiment, described supporting surface the axle girth 22/36 on extend.On supporting surface, be provided with several for example eight Michell type thrust bearing shoes 20.These bearing shells are fixing by a yoke 21, and yoke 21 is at the side surface of the axial thrust bearing shoe that extends beyond two the topmost parts, thereby bearing shell can not be rotated with propelling cam.Described yoke 21 can be dismountable, thereby allows the dismounting thrust bearing shoe, and does not need from thrust-bearing dismounting axle together with propelling cam.Also can replace yoke, perhaps replace with two independent end stops that removably are fixed on the described main bearing with two flanges on the removable section of described main bearing seat.
In the side in the face of described supporting surface, described thrust bearing shoe 20 has an edge that radially extends, thereby bearing shell can be adjusted according to the load from propelling cam about this edge tilt.It is the plane that thrust bearing shoe faces toward on the relative supporting surface of propelling cam at it.
Propelling cam has a slip surface 22 forward, this slip surface rotation symmetry, and be arranged essentially parallel to supporting surface 18 extensions.Under the effect corresponding to the axial force forward of the thrust of propeller cavitation, this slip surface is pressed towards described thrust bearing shoe, and lubricant film is continuously introduced between the supporting surface of this slip surface and thrust bearing shoe simultaneously.Lubricant oil send oil pipe 23 to supply with from one, and this send oil pipe to a U-shaped distribution piping supplying lubricating oil.This distribution piping passes through the radially innermost part of thrust bearing shoe downwards, shown in right side among Fig. 2 is divided.Branch out several jet pipes from this distribution piping, for example by this way to the thrust bearing shoe supplying lubricating oil: an independent jet pipe is arranged at each thrust bearing shoe place.
Above-mentioned thrust bearing shoe only just works when motor 1 is pushed ahead boats and ships.If motor is connected to the screw shaft of a fixing slurry of band apart from propeller cavitation, then need make the motor antiport falling ship time.
When counter-rotating, for absorption axes to backward axle power, described thrust-bearing can be designed to the two-way function thrust-bearing, wherein, described propelling cam also has one second annular slip surface 26, and have corresponding second thrust bearing shoe, 27, the second thrust bearing shoes and be arranged on axially forward the supporting surface of bearing 16 front portions.
On its radially outer periphery, the propelling cam that is shown in Fig. 3 has an arc groove 28, and this groove extends symmetrically around the whole circumference rotation of propelling cam.In all cases, the arcuate shape of this groove all according in the propelling cam for motor main stress situation select.For example, this arcuate shape can be parabola shaped, ellipse, or other suitable curve shapes.
Extend to thrust bearing shoe scope diametrically half in radial direction from the above groove 28 initial position of propelling cam circumference apart from a among Fig. 3.In the embodiments of figure 3, the radial distance of described groove extend through is corresponding to 25% of thrust bearing shoe scope diametrically.For the transmission of high thrust, a benefit can be arranged like this, that is exactly that the big as far as possible part of thrust bearing shoe is by the material supporting solid, inflexibilty in the propelling cam.Described groove has reduced the axial stiffness of propelling cam, thereby, the radially outermost zone elastic bending in the axial direction of propelling cam.
Periphery at propelling cam 14 can be provided with a sprocket wheel 29.Make the toothed rim that is shaped as of this sprocket wheel, its gear ring 30 numbers equal the chain number of chain transmission.Fig. 4 shows an embodiment, and wherein, described sprocket wheel 29 is fixed to one from the radially outstanding flange 31 of the outer surface of propelling cam.Should fixingly connect and implement by bolt.Described sprocket wheel can freely be adjusted in the axial direction together with corresponding flange 31.In the embodiment of Fig. 4, the gear ring 30 of rear-most end has an axial displacement with respect to holding flange 31.Perhaps, a sprocket wheel can be installed, make gear ring 30 axially symmetrical in flange 31 both sides.In this case, sprocket wheel can hot charging to flange, perhaps with radially extending and/or axially extended bolt is connected to its bolt on the flange.
Fig. 5 shows an alternative embodiment, and wherein, described sprocket wheel is divided into two ring parts 32, and wherein each ring part is all on the barrel surface 33 of hot charging to the outer surface of propelling cam.The resilience (mutually resilient) of helping each other in the axial direction of described two ring parts 32.
Fig. 6 shows another embodiment, and wherein, described arc groove 28 ' is positioned on the slip surface 22 relative with thrust bearing shoe 20.This groove 28 ' can perhaps be other any curve shapes that can form suitable stress distribution in material for parabola shaped.When bearing unloaded, radially outermost edge left the distance b of supporting surface on thrust bearing shoe 20.When the bearing full load, the radially outermost zone of propelling cam is subjected to load, makes it to the thrust bearing shoe axial deformation.The size of distortion makes slip surface and supporting surface substantially parallel when full load.
Above-mentioned various embodiments' detailed technology feature can be combined as new embodiment.
Claims (9)
1. internal-combustion engine that is used to drive screw shaft, has a thrust-bearing at the main bearing place of its rear-most end, on the axial direction of bent axle, described main bearing is positioned between the propelling cam of the footstalk of a bent axle (6) and described thrust-bearing, this propelling cam can rotate with described bent axle, thrust bearing shoe (20) be arranged on propelling cam axially forward slip surface and internal-combustion engine base plate (8) described between axially backward the supporting surface of stationary axle bearing of main bearing, it is characterized in that, described propelling cam has a rotational symmetric arc groove (28,28 '), this groove radially inwardly extends to the neutral position of thrust bearing shoe at most.
2. internal-combustion engine as claimed in claim 1 is characterized in that, described arc groove (28 ') inwardly extends to 30% radially outermost place of thrust bearing shoe (20) at most.
3. internal-combustion engine as claimed in claim 1 is characterized in that, described arc groove (28) is positioned on the outer surface of propelling cam.
4. internal-combustion engine as claimed in claim 3 is characterized in that, described arc groove (28) links to each other with at least one freezing mixture supplying pipe.
5. as claim 3 or 4 described internal-combustion engines, it is characterized in that described propelling cam has a radially outstanding flange, a sprocket wheel (29) is fixed on a position that is positioned at the radial outside of described arc groove (28,28 ') on this flange.
6. as claim 3 or 4 described internal-combustion engines, it is characterized in that, described propelling cam has in the axial direction respectively at two barrel surfaces of arc groove (28) both sides, and two ring parts (32) of a sprocket wheel are respectively fixed on the described barrel surface.
7. internal-combustion engine as claimed in claim 6 is characterized in that, the resilience of helping each other in the axial direction of two ring parts of described sprocket wheel.
8. internal-combustion engine as claimed in claim 1 or 2 is characterized in that, described arc groove (28 ') is positioned on the axial slip surface (22) forward of propelling cam.
9. internal-combustion engine as claimed in claim 1 is characterized in that, this internal-combustion engine is the two-stroke crosshead diesel engine that Continuous Maximum Rating is at least 40000kW.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DK200100412A DK200100412A (en) | 2001-03-12 | 2001-03-12 | Combustion engine for propeller shaft drive |
| DKPA200100412 | 2001-03-12 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1374464A CN1374464A (en) | 2002-10-16 |
| CN1223772C true CN1223772C (en) | 2005-10-19 |
Family
ID=8160360
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB021071284A Expired - Fee Related CN1223772C (en) | 2001-03-12 | 2002-03-11 | Internal combustion engine for driving propeller shaft |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP3689378B2 (en) |
| KR (1) | KR100475584B1 (en) |
| CN (1) | CN1223772C (en) |
| DK (1) | DK200100412A (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DK200100412A (en) * | 2001-03-12 | 2002-09-13 | Man B & W Diesel As | Combustion engine for propeller shaft drive |
| DE102010046325A1 (en) * | 2009-10-19 | 2011-05-19 | Schaeffler Technologies Gmbh & Co. Kg | Thrust bearing with offset compensation and drive train with this |
| JP2011179661A (en) * | 2010-03-03 | 2011-09-15 | Mitsubishi Heavy Ind Ltd | Thrust bearing segment |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US112272A (en) * | 1871-02-28 | norris | ||
| JPS61160698A (en) * | 1985-01-07 | 1986-07-21 | Hitachi Ltd | Trust bearing protective device |
| US5110312A (en) * | 1990-05-14 | 1992-05-05 | Outboard Marine Corporation | Releasable roller clutch reversing transmission |
| JP3116233B2 (en) * | 1990-05-17 | 2000-12-11 | 三信工業株式会社 | Thrust receiving structure of ship propulsion machine |
| KR930017249A (en) * | 1992-01-20 | 1993-08-30 | 김광호 | Laser diode manufacturing method |
| DK169927B1 (en) * | 1992-02-19 | 1995-04-03 | Man B & W Diesel Gmbh | Piston engine with a Michell-type thrust bearing |
| KR100214941B1 (en) * | 1997-05-27 | 1999-08-02 | 양재신 | Thrust bearing of automotive crankshaft |
| KR19990030457U (en) * | 1997-12-30 | 1999-07-26 | 양재신 | Structure of Thrust Bearing for Crankshaft Support |
| DK200100412A (en) * | 2001-03-12 | 2002-09-13 | Man B & W Diesel As | Combustion engine for propeller shaft drive |
-
2001
- 2001-03-12 DK DK200100412A patent/DK200100412A/en not_active Application Discontinuation
-
2002
- 2002-03-09 KR KR10-2002-0012673A patent/KR100475584B1/en active IP Right Grant
- 2002-03-11 CN CNB021071284A patent/CN1223772C/en not_active Expired - Fee Related
- 2002-03-12 JP JP2002066360A patent/JP3689378B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JP2002333007A (en) | 2002-11-22 |
| JP3689378B2 (en) | 2005-08-31 |
| KR20020072781A (en) | 2002-09-18 |
| DK200100412A (en) | 2002-09-13 |
| KR100475584B1 (en) | 2005-03-10 |
| CN1374464A (en) | 2002-10-16 |
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| C56 | Change in the name or address of the patentee |
Owner name: MAN DIESEL AS Free format text: FORMER NAME: MAN B + W 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 DIESEL AS |
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| 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: 20051019 Termination date: 20210311 |