EP2253810A1 - Piston pour un cylindre d'un moteur diesel de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour un tel piston - Google Patents

Piston pour un cylindre d'un moteur diesel de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour un tel piston Download PDF

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Publication number
EP2253810A1
EP2253810A1 EP09160834A EP09160834A EP2253810A1 EP 2253810 A1 EP2253810 A1 EP 2253810A1 EP 09160834 A EP09160834 A EP 09160834A EP 09160834 A EP09160834 A EP 09160834A EP 2253810 A1 EP2253810 A1 EP 2253810A1
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EP
European Patent Office
Prior art keywords
piston
lubricant
cylinder
storage space
feed
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.)
Withdrawn
Application number
EP09160834A
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German (de)
English (en)
Inventor
Konrad Räss
Matthias Stark
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wartsila NSD Schweiz AG
Original Assignee
Wartsila NSD Schweiz AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP09160834A priority Critical patent/EP2253810A1/fr
Publication of EP2253810A1 publication Critical patent/EP2253810A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/06—Lubricating systems characterised by the provision therein of crankshafts or connecting rods with lubricant passageways, e.g. bores
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/02—Arrangements of lubricant conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/02—Arrangements of lubricant conduits
    • F01M2011/022—Arrangements of lubricant conduits for lubricating cylinders

Definitions

  • the invention relates to a piston for a cylinder of a large diesel engine and a lubricating device and a lubricating method with such a piston according to the preamble of the independent claim of the respective category.
  • the piston slides on the serving as a running surface surface of the wall of the cylinder, which is usually designed in the form of a cylinder liner (liner) along.
  • a cylinder or piston lubrication is provided.
  • the piston must be as possible on the other hand, the piston must seal the combustion chamber in the cylinder as well as possible, in order to ensure efficient conversion of the energy released during the combustion process into mechanical work.
  • a lubricating oil is usually introduced into the cylinder to achieve good running characteristics of the piston and to minimize the wear of the tread, the piston and the piston rings. Furthermore, the lubricating oil is used to neutralize aggressive combustion products and to prevent corrosion. Because of these many requirements, very high quality and expensive substances are often used as lubricants.
  • lubrication in which the lubricant, typically a lubricating oil, is delivered through the interior of the piston and then through one or more lubrication points provided on the surface of the piston Piston interior is applied to the piston or on the cylinder surface.
  • lubricant typically a lubricating oil
  • a piston for a cylinder of a large diesel engine having a reservoir for receiving a lubricant, with at least one supply line which extends from the reservoir to a lubrication point which is provided on the surface of the piston, and with an infeed, which is designed for releasable connection with a lubricant source, and which opens into the storage space, wherein in the supply line a closing member is provided.
  • the lubrication can be adapted to the duty cycle of the engine without great expenditure on equipment.
  • the reservoir of the piston lubricant is always available and therefore can be applied to the cylinder surface or the piston surface if and only if it is particularly favorable and efficient in relation to the duty cycle. Through this optimization, the amount desw required lubricant or the lubrication rate can be significantly reduced.
  • a conveyor is provided in the piston to convey the lubricant from the storage space through the supply line to the lubrication point.
  • This conveyor serves to increase the pressure in the reservoir of the piston after its filling, so as to allow a discharge of the lubricant through the supply line and the lubrication point.
  • a particularly simple embodiment of apparatus is when the conveyor comprises a delivery piston for the lubricant, the so is configured and arranged that it can be acted upon in the operating state with the combustion chamber side pressure in the cylinder.
  • the cylinder pressure can be used to transport the lubricant to the lubrication point.
  • Another advantageous, simple apparatus measure is when the conveyor comprises a spring-loaded delivery piston to promote the lubricant from the storage space to the lubrication point.
  • the piston has a plurality of piston rings, wherein the lubrication point is arranged between two piston rings with respect to the axial direction defined by the piston axis. Since the lubricant is introduced between the piston rings and not combustion chamber side, that is, with respect to the normal position of use above the first piston ring, an unnecessary burning of the lubricant and the associated adverse coking is at least significantly reduced.
  • the lubricant is distributed by the uppermost, that is, the combustion chamber closest to the piston ring, during the downward movement of the piston and through the lowermost piston ring, the lubricant is distributed in the piston upward movement.
  • the lubricant is partially introduced above, so the combustion chamber side, the uppermost piston ring, resulting in the advantage that a scraping of the lubricant is avoided in the combustion chamber inside.
  • Lubricant passing through the piston rings in the The combustion chamber is moved, namely for lubrication is no longer available and only leads to a strong, unwanted coking.
  • a preferred measure is that a piston ring is provided, which is designed as an oil distributor ring.
  • the primary purpose of this oil distribution ring is to distribute the lubricant with respect to the circumferential direction of the cylinder surface.
  • the oil distribution ring can be arranged between two piston rings, which distribute the lubricant mainly with respect to the axial direction.
  • the closing member in each supply line is preferably designed as a check valve.
  • a locking device is provided, which is designed such that it closes the flow connection between the reservoir and each supply line in cooperation with the lubricant source. In this way it can be ensured that leakage of the lubricant through the supply lines and the lubrication points is avoided during the filling of the storage space.
  • the invention proposes a lubricating device for the cylinder of a large diesel engine comprising a piston according to the invention and a lubricant source with a filling device which is detachably connectable to the feed and cooperates with the piston, that only a lubricant from the lubricant source into the storage space can be introduced when the filling device is connected to the feed.
  • the reservoir of the piston can be filled with lubricant if necessary, wherein the application of the lubricant to the tread of decoupled from this process.
  • the reservoir of the piston is thus filled, but the lubricant is only applied to the tread when it is cheap and efficient with respect to the duty cycle.
  • a variant is that the filling device is arranged so that in the operating state, the feed and the filling device are connected at the bottom dead center of the movement of the piston and separate during the upward movement of the piston.
  • the filling device is arranged so that in the operating state, the feed and the filling device are connected at the top dead center of the movement of the piston and separate during the downward movement of the piston.
  • the invention proposes a lubrication method for the cylinder of a large diesel engine with a reciprocating piston disposed in the cylinder, in which method a supply of the piston is connected during the movement of the piston with a filling device of a lubricant source, a lubricant from the lubricant source the supply is introduced into a reservoir of the piston, the connection between the supply of the piston and the filling device is separated by the movement of the piston, and then the lubricant is brought from the reservoir through a supply line to a lubrication point on the surface of the piston.
  • the lubricant is preferably introduced into the reservoir of the piston when the piston is in the top or bottom dead center of its movement.
  • a large diesel engine which is designed with a piston according to the invention or with a lubricating device according to the invention, or which is operated with a method according to the invention.
  • Fig. 1 Illustrates in a longitudinal sectional view a first embodiment of an inventive piston for a large diesel engine, wherein the piston is generally designated by the reference numeral 1. Furthermore, an embodiment of a lubricant source 2 is shown, which forms an embodiment of a lubricating device 1,2 according to the invention together with the piston 1.
  • the large diesel engine can be designed as a two-stroke or four-stroke engine. In the following reference is made to the case that it is a longitudinally-flushed two-stroke large diesel engine.
  • the piston 1 has a piston axis A, which defines the axial direction, and is arranged in a known manner movable back and forth in a cylinder 3, which has a wall 31 which may be configured as a cylinder insert or liner or as a liner.
  • the inwardly facing surface of the wall 31 forms a tread 32 along which the Piston 1 moved in the operating state.
  • the piston 1 is limited with its upper end according to the illustration a combustion chamber 4, in which the combustion process takes place, and usually has a plurality, here three piston rings 11, 12, 13, which are also referred to as a piston ring package.
  • a lubricant such as a lubricating oil on the tread 32, which lubricates the piston 1, the piston ring package and the tread 32 in order to achieve good running characteristics of the piston 1 and the wear of the cylinder wall, in particular the tread 32, the piston 1 and the piston rings 11, 12, 13 to keep as low as possible.
  • the lubricant is used to neutralize aggressive combustion products and to prevent corrosion, such as sulfur corrosion.
  • the lubricating oil forms on the running surface 32 a lubricating oil film, not shown, which is in constant contact with the piston rings 11, 12, 13.
  • the inventive piston 1 is designed for internal lubrication, that is, the lubricant is applied from the interior of the piston 1 out on the tread 32 and on the lateral surface of the piston 1.
  • a storage space 5 for the lubricant is provided here in the interior of the piston 1, which can be configured as a cavity or as a tank. From this storage space 5, two supply lines 6 designed as bores each extend as far as a lubrication point 61 on the lateral surface of the piston 1.
  • the number of two leads 6 relates only to the axial direction.
  • a plurality of supply lines 6 may be provided at the same axial height. This depends on the need for a shoemaker.
  • a closing member 62 is provided in each case, which is designed here in each case as a pressure holding or check valve 62.
  • Each check valve 62 is designed to block in the direction of the storage space 5, that is, it prevents backflow of the lubricant or other fluids, e.g. of the combustion gas or the scavenging air from the lubrication point 61 into the storage space 5.
  • the valve opens as soon as the pressure difference becomes greater than its opening pressure, which is referred to below as p1.
  • the opening pressure p1 may be the same for the two check valves 61, but it is also possible that each of the check valves 61 has a different opening pressure p1.
  • the lubrication points 6 are arranged with respect to the axial direction defined by the piston axis A between two adjacent piston rings 11, 12, 13, that is, one of the two lubrication points 61 is provided between the first piston ring 11 and the second piston ring 12 and the second lubrication point 61 between the second piston ring 12 and the third piston ring 13 is provided.
  • first piston ring 11 while the one piston ring is meant, which is located closest to the combustion chamber 4.
  • a feed 7 is provided, which is designed here as a feed channel or feed line, and which starts at the underside of the piston 1 according to the illustration and in the Reservoir 5 opens.
  • the feed 7 is designed for detachable connection to the lubricant source 2, as will be explained later.
  • a further closing member 72 is provided, which is configured as a pressure-holding or check valve 72.
  • the check valve 72 prevents with its blocking function a leakage of the lubricant from the reservoir 5 through the feed 7. In the reverse direction, the check valve 72 opens as soon as the applied pressure difference exceeds its opening pressure p2.
  • the lubricant source 2 is arranged stationary with respect to the motor housing and comprises a reservoir 21, in which the lubricant is provided, a filling device 22, which is provided for cooperation with the feed 7, and a pump 23, which supplies the lubricant from the reservoir 21 to the Filling device 22 promotes.
  • the filling device has a closing member 24, which can be configured as a check valve. The closing member 24 prevents leakage of the lubricant from the filling device 22. A possible embodiment of the closing member 24 and the filling device 22 will be explained later.
  • a conveyor 8 is provided to promote the lubricant from the storage space 5 through the leads 6 to the lubrication points 61.
  • the conveyor 8 is designed as a diaphragm piston with a membrane 81.
  • a channel 82 connects, which extends through the piston 1 and above, that is, the combustion chamber side of the first piston ring 11 opens into the surface of the piston 1.
  • the side facing away from the reservoir 5 side of the diaphragm 81 is acted upon by the pressure in the combustion chamber 4 and the pressure in the cylinder above the first piston ring 11.
  • the storage space 5 facing side of the Diaphragm piston 8 is acted upon by the pressure of the lubricant in the reservoir 5.
  • the basic mode of operation of the piston 1 according to the invention is as follows:
  • the lubricant source 2 with the filling device 22 functions as a "filling station" for filling the storage space 5 in the piston.
  • the reservoir 5 in the piston 1 and the lubricant source 2 are cyclically coupled in the lower (or upper) dead center of the piston movement via the feed 7 and the filling device 22, so that during this interaction, the reservoir 5 is filled in the piston 1 with lubricant.
  • the closing member 24, which prevents the lubricant from flowing out of the lubricant source 2, is opened during the coupling or while the infeed 7 and the filling device 22 are connected to one another, so that the lubricant can flow from the lubricant source 2 into the storage space 5.
  • This opening of the closing member 24 can be purely mechanical, or by an electrical, hydraulic or pneumatic control.
  • the pump 23 generates a filling pressure p3, with which the lubricant is conveyed into the storage space 5.
  • the filling pressure is substantially the same pressure as the pressure in the storage space 5 at or immediately after filling.
  • the check valves 62 ensure that no lubricant can pass through the supply lines 6 to the lubrication points 61 when filling the storage space 5.
  • the filling pressure p3 and the opening pressure p1 are set so that the filling pressure p3 is smaller than the smallest opening pressure p1 of the check valves 62.
  • the filling pressure p3 must be greater than the opening pressure p2 of the check valve 72 in the feed 7. The expert knows how such a setting of the pressures p1, p2 and p3 can be realized.
  • Fig. 2 shows a sectional view of the filling device 22 and the closing member 24.
  • the filling device 22 has a filling space 221, in which a coming of the pump 23 supply line 222 opens.
  • a check valve 223 is provided in the supply line 222.
  • the filling space 221 also has a partially conically extending outlet 224, in which a cone 241 of the closing member 24 is located.
  • the cone 241 is pressed by a spring 244 in the conical part of the output 224 so that it in the closed state, the in Fig. 2 is shown, the output 224 closes.
  • the cone 241 has an inner channel 242, which is connected via bores 243 with the outer space of the cone 241.
  • the lubricating oil or the lubricant is pumped through the supply line 222 into the filling space 221 of the filling device 22.
  • the pump 23 introduces the lubricant at the pressure p3 into the filling space 221.
  • a pin 73 is provided with an inner bore at the bottom of the piston 1 at the mouth of the feed 7, so that lubricant can flow through the pin 73 in the feed 7.
  • the pin 73 is formed so that it can penetrate into the outlet 224 of the filling device 22.
  • the check valve 72 prevents leakage of the lubricant through the feed 7.
  • the check valves 62 ensure that during the filling of the reservoir 5 no lubricant passes through the leads 6 to the lubrication points 61. After filling, the lubricant in the reservoir 5 is substantially at the delivery pressure p3, which is smaller than the opening pressure p1 of the check valves 62 and greater than the opening pressure of the check valve 72nd
  • the air is compressed in the cylinder 3 combustion chamber side of the piston 1 during its upward movement.
  • This pressure in the combustion chamber 4 or the combustion chamber side of the first piston ring 11 is also applied to the membrane 81 of the conveyor 8 via the channel 82.
  • This increases the diaphragm piston 8, the pressure in the reservoir 5. If the pressure has risen so far that the pressure difference across the check valves 62 is greater than the opening pressure p1 of the check valves 62, so they open and the lubricant passes through the leads 6 to the lubrication points 61 and from there to the tread 32. The lubrication begins.
  • the diaphragm piston 8 is adjusted so that it reacts as accurately as possible above a specified pressure. This makes it possible for the lubricant to be introduced into the cylinder 3 exactly where it is needed or where it is most efficient.
  • the opening of the channel 82 is chosen sufficiently large that it does not come to a coking of this opening during operation. A coking is further prevented by the fact that the lubricant is injected not above, so the combustion chamber side of the first piston ring 11, but between the piston rings 11, 12, 13. This ensures safe operation.
  • the diaphragm piston 8 is designed so that it above the specified pressure on its piston displacement displaced as accurately as possible predetermined amount of lubricant from the reservoir 5 and presses on the leads 6 in the piston ring package.
  • this ensures a load-dependent lubrication.
  • Fig. 3 shows a diagram with the pressure curve p in the cylinder 3 in dependence on the crank angle KW, which is plotted on the horizontal axis.
  • the piston 1 At the crank angle 0 and at the crank angle 360 °, the piston 1 is in the lower reversal point, that is, where the filling of the storage space 5 takes place.
  • ps that limiting pressure in the cylinder is designated, in which the pressure drop across the check valves 62 is just as large as the opening pressure p1 of the check valves 62.
  • the Limit pressure ps so lubricant is conveyed from the storage space 5 through the leads 6 to the lubrication points 61, it is smaller than the limit pressure ps, so no lubricant can pass through the leads 6 to the lubrication points 61.
  • the solid curve in Fig. 3 shows the pressure curve for a medium load range of the large diesel engine, while the dashed curve shows the pressure curve at higher load.
  • the pressure in the cylinder 3 is higher than the limit pressure ps.
  • the area under the curve above the limit pressure ps describes the load dependency of the lubricant quantity. This load dependency can be coupled with the calculation of the mean effective pressure.
  • the closing process in which the lubrication is terminated by closing the check valves 62, crank angle moderately shifts to later (higher) values.
  • the diaphragm piston 8 For the supply of the lubricant by means of the diaphragm piston 8, it is possible to work with a constant stroke of the diaphragm piston 8. If then the limiting pressure ps is exceeded at the crank angle W1, the lubricant passes at a constant delivery rate to the lubrication points 61 until the pressure in the cylinder 3 falls below the value ps again.
  • Another possibility is to design the diaphragm piston 8 as a proportional piston, so that the amount of lubricant that is conveyed between the crank angles W1 and W2 per time follows the pressure curve in the cylinder.
  • the diaphragm piston 8 is designed such that its stroke or the distance traveled by it follows the pressure in the cylinder 3.
  • the two diagrams below show the flow rates F1 and F2 of lubricant as a function of the crank angle KW.
  • the flow rate F1 corresponds to the variant with a constant stroke of the diaphragm piston 8
  • the flow rate F2 shows the case when the stroke of the diaphragm piston 8 follows the pressure curve in the cylinder 3.
  • the amount of lubricant introduced into the cylinder 3 can be adjusted very precisely, and the time or the time interval of the lubrication can be controlled very precisely. This results in a very efficient use of the lubricant, resulting in a very low consumption results. Lubricating rates of, for example, 0.6 g / kWh can be achieved.
  • the storage space 5 does not have to be filled every working cycle, so not every time the piston 1 is at bottom dead center.
  • the pump 23 of the lubricant source 2 can be controlled so that it promotes lubricant only in every second, or third, or fourth, etc. work cycle in the reservoir. It is also possible to monitor the filling level of the storage space 5 with a sensor and only if necessary to control the pump 23 in such a way that lubricant is conveyed into the storage space.
  • other conveyors 8 may be provided, for example, hydraulic, pneumatic, electrical or combinations thereof, after filling the storage space 5 and after decoupling of the feed 7 from the filling device 22, the pressure in the storage space 5 to a predetermined Increase crank angle or time so that the opening pressure p1 of the check valves 62 is exceeded and the lubrication starts.
  • lubrication points 61 are possible.
  • a piston ring can be configured for example as an oil distributor ring.
  • Fig. 5 shows a second embodiment of a piston 1 according to the invention and a lubricant source 2. From the function of equal or equivalent parts are provided with the same reference numerals as in Fig. 1 , In the following, the differences to the first embodiment are mainly discussed. ⁇ All explanations, which were made in connection with the first embodiment of the inventive piston 1, apply in an analogous or analogous manner to the same for the second embodiment.
  • the reservoir 5 is designed as a tank which is arranged in a cavity 51 in the interior of the piston 1.
  • the storage space 5 has in its wall two outlet openings 52 through which the lubricant can pass from the storage space 5 into the supply lines 6.
  • a delivery piston 8 is provided as a conveyor 8, which is supported by a spring 83 at the upper end of the storage space 5 as shown.
  • the delivery piston 8 is moved upward in accordance with the representation of the force of the spring 83. Due to the spring tension thus generated, the delivery piston 8 moves after the Filling process as shown below and thereby presses the lubricant through the leads 6 and the lubrication point 61 in the piston ring package.
  • the feed 7 is integrated into the storage space 5 and has the check valve 72.
  • the feed 7 it is also possible in the second embodiment to design the feed 7 as a feed channel or line or bore and / or a pin 73 as in Fig. 2 to be shown provided.
  • the storage space 5 is arranged movably in the cavity 51 with respect to the axial direction and is supported by a return spring 9 at the end of the cavity 51, which faces the combustion chamber 4.
  • the delivery piston 8 When filling the storage space 5, the delivery piston 8 must be tensioned against the force of the spring 83. This means that the filling pressure p3 must be at least as great as the maximum pressure that the delivery piston 8 can exert on the lubricant due to its spring loading. In order for this maximum pressure is sufficient to open the check valves 62 in the supply lines 6 for lubrication, it must be greater than the opening pressure p1 of the check valves 62. Without a locking device for closing the supply lines 6, this would mean that even when filling the Vorratsraums 5 at least a portion of the lubricant passes directly through the leads 6 to the lubrication points 61 and exits there. This prevents the locking device as now based on the Fig. 6 is explained. Fig.
  • FIG. 6 shows the locking device in the left view in the open position and in the right view in the closed position, which is taken during the filling process.
  • the filling of the storage space 5 is carried out in a similar manner as described in connection with the first embodiment.
  • the delivery piston 8 is tensioned in the storage space 5, that is, it is moved against the force of the spring 83 as shown above.
  • the piston 1 moves upward and the storage space 5 loses contact with the lifting device 25, characterized moves the storage space 5 by the spring force of the return spring 9 relative to the piston 1 as shown below and takes the in Fig. 6 in the left illustration shown position.
  • the outlet openings 52 are aligned with the supply lines 6, so that lubricant can now pass from the storage space 5 through the outlet openings 52 into the supply lines 6 and to the lubrication points 61.
  • the second embodiment a different characteristic of the introduction of the lubricant in the piston ring package.
  • the introduction of the lubricant takes place here, as long as the pressure in the cylinder below a limit pressure ps remains.
  • the lowest pressure namely substantially the scavenging air pressure.
  • the pressure drop across the check valves 62 is then essentially determined by the difference between the pressure generated by the delivery piston 8 in the storage space 5 and the cylinder side on the check valves 62 pressure corresponding approximately to the scavenging pressure.
  • FIG. 7 This illustrates Fig. 7 in one too Fig. 3 analog representation in which the pressure p in the cylinder in dependence on the crank angle KW for a duty cycle and for a load condition of the engine is shown.
  • the lubrication takes place in the hatched areas. In the area around the bottom dead center, ie at the crank angles 0 ° and 360 °, there is no lubrication, as the two small vertical lines in Fig. 7 indicate, because during the filling process of the storage space 5, the supply lines 6 are closed by the locking device relative to the storage space 5.
  • this second embodiment there is another way of supplying lubricant, because here the lubrication takes place mainly in the lower region of the running surface 32 of the cylinder 3. This also results in a changed characteristic of the flow rate F of the lubricant.
  • Fig. 8 for the second embodiment in a too Fig. 4 shown analog representation.
  • first embodiment and the second embodiment are combined with each other.
  • two storage spaces 5 can be provided and two lubricating sources 2, wherein one of the storage spaces 5 is filled and emptied as described for the first embodiment and the other storage space 5 as described for the second embodiment.
  • Fig. 9 shows a sectional view of the piston ring package with the piston rings 11, 12 and 13.
  • the leads 6 On the representation of the leads 6 was in Fig. 9 omitted, they are preferably arranged so that the lubrication points 61 are arranged as described above in each case between two adjacent piston rings.
  • first piston ring 11 and the third piston ring 13 are each designed spherically but asymmetrically.
  • the first piston ring 11 is designed rounded on its side facing away from the combustion chamber 4 and the third piston ring 13 is rounded on its side facing the combustion chamber 4.
  • the first piston ring 11 distributes the lubricant in the downward movement of the piston 1.
  • This has the advantage that no lubricant is scraped into the combustion chamber 4 and so that it gets lost for lubrication. As a result, the lubricant consumption can be reduced.
  • a strong coking is counteracted, whereby, for example, the use of an anti-polishing ring "can be unnecessary.
  • the third piston ring 13 distributes the lubricant on the running surface 32.
  • a further advantageous measure is to design the second piston ring 12, which is arranged between the other two piston rings 11 and 13, as an oil distribution ring.
  • the oil distribution ring serves to distribute the lubricant over the circumference of the tread 32.
  • One possible embodiment is in the 10 and 11 shown.
  • Fig. 10 shows a side view of the oil distribution ring designed as a piston ring 12
  • Fig. 11 a plan view of the piston ring 12.
  • the piston ring has on its outer surface, in the operating state of the wall 31 of the cylinder 3, a plurality of inclined grooves 122, of which in 10 and FIG. 11 only one is shown.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP09160834A 2009-05-20 2009-05-20 Piston pour un cylindre d'un moteur diesel de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour un tel piston Withdrawn EP2253810A1 (fr)

Priority Applications (1)

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EP09160834A EP2253810A1 (fr) 2009-05-20 2009-05-20 Piston pour un cylindre d'un moteur diesel de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour un tel piston

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Application Number Priority Date Filing Date Title
EP09160834A EP2253810A1 (fr) 2009-05-20 2009-05-20 Piston pour un cylindre d'un moteur diesel de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour un tel piston

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EP09160834A Withdrawn EP2253810A1 (fr) 2009-05-20 2009-05-20 Piston pour un cylindre d'un moteur diesel de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour un tel piston

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2672082A1 (fr) 2012-06-05 2013-12-11 Wärtsilä Schweiz AG Dispositif de collecte de lubrifiant
EP2682572A1 (fr) 2012-07-04 2014-01-08 Wärtsilä Schweiz AG Système de lubrification

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US2843221A (en) * 1955-05-04 1958-07-15 Nickles Machine Corp Force feed lubricating device for pistons
JPH029903A (ja) * 1988-06-27 1990-01-12 Mitsubishi Heavy Ind Ltd シリンダ油注油機構
JPH05163918A (ja) * 1991-12-13 1993-06-29 Mitsubishi Heavy Ind Ltd リング・ライナ注油装置
JPH0783015A (ja) * 1993-09-10 1995-03-28 Mitsubishi Heavy Ind Ltd ピストン連動式注油装置
JPH07208134A (ja) * 1994-01-14 1995-08-08 Mitsubishi Heavy Ind Ltd シリンダ注油装置
EP0903473A1 (fr) 1997-09-22 1999-03-24 Wärtsilä NSD Schweiz AG Moteur diesel et méthode de fonctionnement
US20080041346A1 (en) * 2006-06-22 2008-02-21 Advanced Propulsion Technologies, Inc. Piston ring, piston skirt and cylinder liner lubrication system and method for an internal combustion engine

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Publication number Priority date Publication date Assignee Title
EP2672082A1 (fr) 2012-06-05 2013-12-11 Wärtsilä Schweiz AG Dispositif de collecte de lubrifiant
EP2682572A1 (fr) 2012-07-04 2014-01-08 Wärtsilä Schweiz AG Système de lubrification

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