EP2273078A1 - Piston pour un cylindre d'un moteur de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour ce piston - Google Patents

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

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Publication number
EP2273078A1
EP2273078A1 EP10165750A EP10165750A EP2273078A1 EP 2273078 A1 EP2273078 A1 EP 2273078A1 EP 10165750 A EP10165750 A EP 10165750A EP 10165750 A EP10165750 A EP 10165750A EP 2273078 A1 EP2273078 A1 EP 2273078A1
Authority
EP
European Patent Office
Prior art keywords
piston
lubricant
cylinder
storage space
pressure
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Withdrawn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
EP10165750A
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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 EP10165750A priority Critical patent/EP2273078A1/fr
Publication of EP2273078A1 publication Critical patent/EP2273078A1/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Withdrawn legal-status Critical Current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
    • F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F3/00—Pistons 
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F5/00—Piston rings, e.g. associated with piston crown
    • 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
    • F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
    • F01M2001/083—Lubricating systems characterised by the provision therein of lubricant jetting means for lubricating cylinders
    • 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 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.
  • Large engines especially in the design as large diesel engines, which may be configured as two-stroke or four-stroke internal combustion engines, are often used as drive units for ships or in stationary operation, e.g. used to drive large generators for generating electrical energy.
  • the large engines usually run for long periods in continuous operation, which places high demands on the reliability and availability. Therefore, for the operator in particular long maintenance intervals, low wear and an economical handling of the operating materials are central criteria.
  • 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 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.
  • a proven method is the so-called internal lubrication, in which the lubricant, typically a lubricating oil, is conveyed through the interior of the piston and then via one or more lubrication points, which are provided on the surface of the piston, from the piston interior to the piston and the cylinder surface is applied.
  • the lubricant typically a lubricating oil
  • the lubricating oil is supplied to the piston via a conveyor, which is actuated by the movement of the crosshead.
  • a lubricant delivery device is proposed, by means of which the lubricant can be introduced into the piston.
  • a lubricant line is arranged in the piston, which leads to the uppermost piston ring.
  • a lubricant chamber is arranged, in which the lubricant can be pressurized by means of a spring-loaded pressure piston. This pressure corresponds to the injection pressure.
  • spring-loaded slide valve Between the lubricant chamber and the lubricant outlet on the top piston ring is spring-loaded slide valve, which can be actuated by the pressure in the cylinder chamber. When the pressure in the piston chamber exceeds the spring pressure acting on the slide valve, the slide valve opens a communication path in the lubricant line and lubricant is delivered from the lubricant chamber to the uppermost piston ring.
  • a piston for a cylinder of a large engine which has a piston body which contains a reservoir for receiving a lubricant, wherein the piston body is peripherally bounded by a piston skirt, wherein the reservoir is connected via a lubricant line with the piston skirt, and an infeed is provided, which is designed for releasable connection with a lubricant source, wherein the feed opens into the reservoir and wherein the lubricant line opens into a lubricant collecting element, wherein the lubricant collecting element is formed as a piston ring having an annular body.
  • the annular body of the lubricant collecting element has at least one groove delimited by two lips.
  • the lips are advantageously in touching contact with the tread so that lubricants are spread on the tread as well as being removed from the tread.
  • 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.
  • the lubricant collecting element By means of the lubricant collecting element, the lubricant located on the running surface is collected and removed via an opening in the lubricant collecting element. This optimization can also significantly reduce the amount of lubricant required or the lubrication rate.
  • the lubricant which has been removed by means of the lubricant collecting element, passes through a lubricant line into the reservoir and is thus available for further lubrication.
  • a lubricant removal device can be provided, which is connectable to the lubricant line.
  • a supply line is provided, which extends from the storage space to a lubrication point, which is provided on the surface of the piston, so that lubricant from the storage space to the lubrication point can be conducted, wherein in the supply line a closing member is provided.
  • a delivery device can be provided in the piston in order 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.
  • the conveyor comprises a delivery piston for the lubricant, which is configured and arranged so that it can be acted upon in the operating state with the combustion chamber side pressure in the cylinder.
  • the pressure in the combustion chamber of the cylinder can be used to transport the lubricant to the lubrication point.
  • 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 on the combustion chamber side, ie with respect to the normal position of use above the first piston ring, or over the lubricant collecting element, 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 next to the nearest piston ring, in 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, This results in the advantage that scraping of the lubricant into the combustion chamber is avoided.
  • Lubricant which is moved by the piston rings in the combustion chamber, namely for lubrication is no longer available and only leads to a strong, unwanted coking.
  • the piston skirt encloses a piston surface at a first end, that is to say the piston skirt represents the edge of the piston surface.
  • This piston surface adjoins the combustion chamber, wherein the lubricant collecting element is preferably arranged outside the piston ring furthest away from the combustion chamber on the piston skirt.
  • a preferred measure is that a piston ring is provided, which is designed as a lubricant distributor ring.
  • the primary purpose of this lubricant distributor ring is to distribute the lubricant with respect to the circumferential direction of the cylinder surface.
  • the lubricant distribution ring can be arranged between two piston rings, which distribute the lubricant mainly with respect to the axial direction.
  • a closing member may be provided in the lubricant line. This arrangement is particularly advantageous when the lubricant line is used as a supply and discharge for lubricant.
  • the closing member may in particular be set such that it has a Opening pressure of 1 to 5 bar, preferably 2 to 5 bar, more preferably around 4 bar. In this case, the closing member remains closed to the pressure in the cylinder space, as long as it is not opened by means of a lifting device to drain lubricant or supply lubricant.
  • a closing member may be provided in each of the supply lines.
  • the closing member in each supply line and in the lubricant 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 engine, comprising a piston according to the invention, wherein the piston skirt is surrounded by a lubricating space for lubricating a running surface of a cylinder, and a lubricant source with a filling device which is detachably connectable to the feed and so cooperates with the piston, that only a lubricant from the lubricant source into the reservoir can be introduced when the filling device is connected to the feed, wherein the reservoir is connectable to a lubricant collecting element, so that lubricant is traceable from the lubricating space in the storage room.
  • the reservoir of the piston can be filled with lubricant as needed, with the application of the lubricant to the tread and the collection of lubricant from the tread being 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.
  • lubricant which is passed from the lubricant collecting element into the storage space, can be removed from the storage space via a lubricant removal device which can be docked to the feed.
  • contaminated lubricant can be removed from the storage space and the supply lines and replaced by correspondingly pure lubricant.
  • a variant is that the filling device or the lubricant removal device are arranged so that in the operating state, the feed and the filling device or lubricant removal 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 or lubricant removal device is arranged so that in the operating state, the feed and the filling device or lubricant removal device are connected at 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 engine with a reciprocating piston arranged in the cylinder, in which method a supply of the piston during the movement of the piston is connected to a filling device of a lubricant source, a lubricant from the lubricant source is introduced by the feed into a reservoir of the piston, the connection between the feed 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 piston skirt.
  • 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 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 engine, in particular 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 piston moves substantially in a bore of the cylinder
  • the inwardly facing surface of the wall 31 forms a running surface 32, along which the piston 1 moves 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 reservoir 5 for the lubricant which can be designed as a cavity or as a tank. From this storage space 5, two supply lines 6 designed as bores each extend up to a lubrication point 61 on the piston skirt 16 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. The number of supply lines depends on the need for a shoe.
  • 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 such that it blocks in the direction of the storage space 5, that is, it prevents a backflow of the lubricant or other fluids, such as the combustion gas or the scavenging air from the Lubrication point 61 in the reservoir 5.
  • the valve opens as soon as the pressure difference is greater than its opening pressure, which is hereinafter referred to 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 representation of the underside of the piston 1 and opens into the storage space 5.
  • 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 outflow of the lubricant the supply chamber 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 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 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 chamber 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 storage space 5 in the piston 1 and the lubricant source 2 are cyclically in the lower (or in the top) dead center of the piston movement via the feed 7 and the filling device 22 coupled, so that during this interaction, the storage space 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 storage space 5 is connected via a lubricant line 10 with the piston skirt 16, wherein the lubricant line 10 opens into a lubricant collecting element 14.
  • a lubricant collecting element 14 is arranged in an annular recess 19 of the piston skirt.
  • the lubricant collecting element 14 is thus according to Fig. 1 a piston ring having an annular body 20 which preferably has at least one groove 28 delimited by two lips 26, 27.
  • the lips 26, 27 are in touching contact with the running surface 32. Between the lips, the outer peripheral groove 28 is formed.
  • the lips 26, 27 thus form the mating surface of the lubricant collecting element 14 which slides along the running surface 32 and which is in frictional contact with the running surface 32.
  • the lubricant collecting element 14 in the operating state can collect and store lubricant in the recess 19, so that locally excess lubricant can be collected. This collected lubricant is no longer available on the tread 32, but can if necessary Locations that have an increased lubricant requirement, are applied again from the recess on the cylinder surface.
  • the lubricant collecting element 14 thus functions not only as a collecting element for the lubricant in the operating state of the large diesel engine, but also can remove lubricant from the running surface. In this function, it is similar to a lubricant scraper.
  • the lubricant collecting element 14 also has a function as a lubricant distribution element.
  • the body 29 may include an opening 30 through which lubricant from a source of lubricant may be introduced into the groove 28 of the lubricant collection element or, conversely, excess lubricant may be withdrawn from the tread 32.
  • the lubricant collecting element is in touching contact with the running surface 32 because it performs a sealing function against gas from the cylinder space 20 containing the crankshaft.
  • this cylinder chamber 20 is also referred to as a receiver space containing fresh air, which is usually provided by a turbocharger, not shown.
  • the pressure of the fresh air which is supplied via scavenging ports to the combustion chamber 4 when the piston 1 is in the range of bottom dead center.
  • the fresh air is under overpressure, which is usually in the range of 1 to 5 bar, preferably 2 to 5 bar, in particular, for example, the 4 bar.
  • a spring element 33 may be provided, which is located between the recess 19 and the body 29 of the lubricant collecting element.
  • 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 further 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 into the filling space 221 with a filling pressure p3.
  • 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 an outlet of the filling device 22.
  • 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 filling 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 in the cylinder 3 is compressed on the combustion chamber side of the piston 1 during its upward movement.
  • This pressure in the combustion chamber 4 or on 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 is a load-dependent lubrication guaranteed.
  • 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 the pressure in the cylinder 3, so the pressure on the combustion chamber side of the first piston ring 11 is meant higher is referred to as 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 that 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 may be configured, for example, as a lubricant distributor ring.
  • a lubricant collecting element 14 may be provided in place of each piston ring, with the exception of the piston ring nearest the combustion chamber 4.
  • 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 that 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.
  • Delivery piston 8 is provided, which is supported by a spring 83 at the illustration according to the upper end of the storage space 5.
  • the delivery piston 8 is moved upward in accordance with the representation of the force of the spring 83.
  • the delivery piston 8 moves downwards as shown in the illustration after the filling process and thereby presses the lubricant through the supply lines 6 and the lubrication point 61 into 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 storage space 5 designed as a tank functions together with the restoring spring 9 as a blocking device which, in cooperation with the lubricant source 2, closes the flow connection between the storage space 5 and each supply line 6, as will be explained in more detail below.
  • 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 Reservoir 5 at least a portion of the lubricant directly passes 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. 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 limited by the delivery piston 8 and the reservoir 5 compensation chamber 45 may in particular contain a compressible medium.
  • the delivery piston 8 is provided at its periphery with a sealing element 46 which fluid-tightly separates the compensation chamber 45 from the reservoir, which contains the lubricant.
  • the lifting device 25 is designed for example as a stop against which the storage space 5 starts before the closing member 24 of the filling device 22 is opened.
  • 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,
  • the reservoir 5 moves 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 remains below a limit pressure ps.
  • 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.
  • 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.
  • a further variant for both embodiments is that the filling of the storage space 5 takes place in a similar manner in the same way when the piston is at top dead center.
  • 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 crowned but asymmetrical.
  • 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.
  • the third piston ring 13 distributes the lubricant on the running surface 32.
  • a lubricant distributor ring serves to distribute the lubricant over the circumference of the tread 32.
  • the lubricant 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 designed as a lubricant distributor ring piston ring 12 and Figure 11 a plan view of the piston ring 12.
  • the piston ring has on its outer circumferential surface, which faces 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.
  • Fig. 12 shows a third embodiment of the inventive piston.
  • the piston 1, of which only a part is shown, carries the reference numeral 1 as in the preceding embodiments. Furthermore, a lubricant extraction device 40 is shown schematically. This lubricant removal device is optionally by a Lubricant source 2 replaceable, as described in connection with the first or second embodiment.
  • An essential difference from the preceding embodiments is that the storage space 5 contains no conveyor 8 by means of which lubricant is passed between two piston rings 11,12,13 via a supply line into the lubricating space.
  • the lubricating space extends between the piston skirt 16 and the running surface 32 on the wall 31 of the cylinder 3.
  • the lubricant is distributed via the lubricant collecting element 14 in the lubricating space and removed via the lubricant collecting element 14 from the lubricating space and fed via the lubricant line 10 to the storage space 5.
  • the storage space 5 is a reservoir filled with lubricant, which is arranged in the piston body 34. From the storage space 5 leads on the one hand at least one lubricant line 10 to the lubricant collecting element 14 and at least one feed 7 to the cylinder chamber 20.
  • a closing member 72 is arranged to prevent that contained in the reservoir 5 lubricant can run unintentionally into the cylinder chamber.
  • the closing member 72 is designed in particular as a check valve.
  • a lubricant source (not shown, can be connected, the operation of the in Fig. 1 and Fig. 2 corresponds to the lubricant source shown.
  • the lubricant source can be introduced periodically or if necessary lubricant into the storage space 5.
  • a measuring device can be arranged, which provides a measurement of the state of the lubricant in the reservoir, for example, measures the pressure of the lubricant. If the measured value falls below a threshold value, the lubricant source is connected to the feed 7.
  • a measuring device can be arranged in the lubricating space, which provides a relevant for the amount and the condition of the lubricant characteristic.
  • the introduction of the lubricant into the lubricating space is similar to that described in connection with the second embodiment as long as the pressure in the lubricating space remains below a limiting pressure, which is also to be referred to here as ps.
  • a limiting pressure which is also to be referred to here as ps.
  • the lowest pressure is present at the lubricant collecting element, namely essentially the pressure in the cylinder chamber 20, that is to say the scavenging air pressure.
  • the pressure of the lubricant is higher than the pressure in the cylinder space and the pressure drop across the lubricant collecting element 14 and the lubricant line 10. Accordingly, lubricant flows from the storage space 5 into the lubricating space. This lubricant flow continues until the pressure in the lubricant chamber reaches the limit pressure ps, ie equal to the pressure in the reservoir 5 plus the pressure drop across the lubricant collecting element 14 and the lubricant line 10.
  • the lubricant collecting element fulfills a function as a lubricant distribution element below the limit pressure. If the piston now moves further in the direction of top dead center, the increasing internal pressure in the lubricant chamber prevents the escape of lubricant from the lubricant Lubricant collecting element.
  • the lubricant collecting element acts as a collecting element above the limit pressure ps, that is, the two lips 26, 27 detect lubricant in the lubricant space and guide it into the opening 30, into the lubricant line 10 and into the storage space 5. This measure prevents lubricant is entered into the combustion chamber 4 and on the other hand it is ensured that sufficient lubricant is present in the lubricant space.
  • a Lubricant removal device 40 are connected to the feed 7 .
  • the lubricant extraction device 40 includes an opening member to move the Closing member 72 to open mechanically. Since the lubricant is under a pressure which is higher than the pressure in the cylinder chamber 20, flows in a working under atmospheric pressure lubricant removal device lubricant from the reservoir 5 and any lubricant in the lubricant line 10 or in the lubricant collecting element 14 located. To increase the outflow rate, the lubricant extraction device can also operate under a pressure that is less than the atmospheric pressure.
  • the lubricant can be drained off via the feed 7 or in addition to the same via another, not shown drain line.
  • a plurality of such drain lines may be provided at different locations of the piston body, in particular when the storage space 5 is annular or opens into an annular channel extending in the piston body, from which a plurality of lubricant lines branches, leading to a plurality of lubricant collecting elements.
  • lubricant collecting elements between each two piston rings.
  • the placement of the lubricant collecting elements depends on the need for lubricant on the piston skirt 16 and the associated running surface 32.
  • the lubricant collecting elements can be distributed along the circumference of the piston skirt, in particular be arranged at equal distances from each other.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
EP10165750A 2009-07-09 2010-06-11 Piston pour un cylindre d'un moteur de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour ce piston Withdrawn EP2273078A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP10165750A EP2273078A1 (fr) 2009-07-09 2010-06-11 Piston pour un cylindre d'un moteur de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour ce piston

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP09165085A EP2133520A1 (fr) 2009-07-09 2009-07-09 Piston pour un cylindre d'un moteur de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour ce piston
EP10165750A EP2273078A1 (fr) 2009-07-09 2010-06-11 Piston pour un cylindre d'un moteur de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour ce piston

Publications (1)

Publication Number Publication Date
EP2273078A1 true EP2273078A1 (fr) 2011-01-12

Family

ID=41100470

Family Applications (2)

Application Number Title Priority Date Filing Date
EP09165085A Withdrawn EP2133520A1 (fr) 2009-07-09 2009-07-09 Piston pour un cylindre d'un moteur de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour ce piston
EP10165750A Withdrawn EP2273078A1 (fr) 2009-07-09 2010-06-11 Piston pour un cylindre d'un moteur de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour ce piston

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP09165085A Withdrawn EP2133520A1 (fr) 2009-07-09 2009-07-09 Piston pour un cylindre d'un moteur de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour ce piston

Country Status (5)

Country Link
EP (2) EP2133520A1 (fr)
JP (1) JP5689615B2 (fr)
KR (1) KR20110005218A (fr)
CN (1) CN101956628B (fr)
BR (1) BRPI1002667A2 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2410140B1 (fr) * 2010-07-20 2013-05-08 Wärtsilä Schweiz AG Dispositif de lubrification pour un piston
DK2484875T3 (en) 2011-02-04 2014-02-24 Waertsilae Nsd Schweiz Ag Cylinder lubrication device
EP2672082A1 (fr) 2012-06-05 2013-12-11 Wärtsilä Schweiz AG Dispositif de collecte de lubrifiant
CN103527282B (zh) 2012-07-04 2017-06-30 瓦锡兰瑞士公司 润滑系统、润滑剂注入元件、内燃发动机以及润滑方法
DK178468B1 (en) * 2014-09-19 2016-04-11 Man Diesel & Turbo Deutschland A top piston ring for a large two-stroke turbo-charged uniflow-scavenged internal combustion engine with crossheads
FR3054622B1 (fr) * 2016-08-01 2018-08-03 Peugeot Citroen Automobiles Sa Ensemble piston bielle rotulee avec passage d’huile par une contre-rotule
DE102017007639A1 (de) 2017-08-12 2019-02-14 Daimler Ag Anordnung eines Kolbens in einem Zylinder für eine Hubkolbenmaschine, insbesondere eines Kraftfahrzeugs
EP3724463B1 (fr) * 2017-12-13 2024-01-31 Hans Jensen Lubricators A/S Un injecteur pour un gros moteur lent à deux temps et procédé de lubrification d'un tel moteur, ainsi qu'un tel moteur
CN109910805A (zh) * 2019-03-22 2019-06-21 安徽彤上智能科技有限公司 一种低损耗防撞梁
GB201916126D0 (en) * 2019-11-06 2019-12-18 Dice Ind Ltd An internal combustion engine

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR422386A (fr) * 1910-11-10 1911-03-20 Maurice Lender Dispositif de graissage des parois des cylindres dans les machines motrices de toute nature
JPS5887948U (ja) * 1981-12-11 1983-06-15 トヨタ自動車株式会社 内燃機関のピストン冷却装置
JPS58150060A (ja) * 1982-03-01 1983-09-06 Kawasaki Heavy Ind Ltd 内燃機関のピストン構造
JPH029903A (ja) 1988-06-27 1990-01-12 Mitsubishi Heavy Ind Ltd シリンダ油注油機構
EP0903473A1 (fr) 1997-09-22 1999-03-24 Wärtsilä NSD Schweiz AG Moteur diesel et méthode de fonctionnement
JP2007278228A (ja) * 2006-04-10 2007-10-25 Toyota Motor Corp 内燃機関
JP2008101594A (ja) * 2006-10-20 2008-05-01 Toyota Motor Corp ピストンの潤滑油供給構造及びピストンリング

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03112554U (fr) * 1990-03-06 1991-11-18
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
ATE556256T1 (de) * 2006-12-18 2012-05-15 Waertsilae Nsd Schweiz Ag Kolben mit einem ölsammelring

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR422386A (fr) * 1910-11-10 1911-03-20 Maurice Lender Dispositif de graissage des parois des cylindres dans les machines motrices de toute nature
JPS5887948U (ja) * 1981-12-11 1983-06-15 トヨタ自動車株式会社 内燃機関のピストン冷却装置
JPS58150060A (ja) * 1982-03-01 1983-09-06 Kawasaki Heavy Ind Ltd 内燃機関のピストン構造
JPH029903A (ja) 1988-06-27 1990-01-12 Mitsubishi Heavy Ind Ltd シリンダ油注油機構
EP0903473A1 (fr) 1997-09-22 1999-03-24 Wärtsilä NSD Schweiz AG Moteur diesel et méthode de fonctionnement
JP2007278228A (ja) * 2006-04-10 2007-10-25 Toyota Motor Corp 内燃機関
JP2008101594A (ja) * 2006-10-20 2008-05-01 Toyota Motor Corp ピストンの潤滑油供給構造及びピストンリング

Also Published As

Publication number Publication date
BRPI1002667A2 (pt) 2012-03-27
JP5689615B2 (ja) 2015-03-25
EP2133520A1 (fr) 2009-12-16
CN101956628B (zh) 2014-12-17
JP2011017336A (ja) 2011-01-27
CN101956628A (zh) 2011-01-26
KR20110005218A (ko) 2011-01-17

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