KR20180020106A - Cylinder lubrication apparatus for a large two-stroke compression-ignited internal combustion engine - Google Patents

Abstract

The present invention relates to a cylinder lubrication apparatus for a large two-stroke uniflow compression-ignition internal combustion engine, capable of adjusting a feeding speed. According to the present invention, the apparatus comprises: a plurality of piston pumps including a dosing plunger (70) disposed in each dosing cylinder (71) to be able to slide, wherein each dosing cylinder (71) includes a pump chamber (72) fluidly connected to a pump outlet (62) for fluid connection to one of the injectors (24); a common driving unit (80) to simultaneously operate all dosing plungers (70); a hydraulic linear actuator (83) operably connected to the common driving unit (80); and a means to adjust the stroke length of the common driving unit (80) to any one of at least two preset individual lengths (L1, L2) during operation of the cylinder lubrication apparatus (55).

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a cylinder lubrication apparatus for a large two-stroke compression ignition internal combustion engine,

The present disclosure relates to a cylinder lubrication apparatus for a large two-stroke uniflow compression ignition internal combustion engine, and more particularly to an apparatus for supplying a cylinder lubrication liquid to an inner surface of a cylinder liner of a large two stroke full-stroke compression ignition internal combustion engine.

Large Two-stroke Single-Turbo Turbocharged Compression Ignition Internal combustion crosshead engines are commonly used as propulsion systems for large ships and as prime movers for power plants. With enormous size, weight and power output, this engine is very different from a conventional combustion engine, and a large two-stroke turbocharged compression internal combustion engine is itself categorized as one class.

Large two-stroke compression ignition internal combustion engines are traditionally operated with liquid fuels such as fuel oil or heavy oil, which, in particular, operate with heavy fuel oil at low cost. In heavy oil, a large amount of particles harmful to the engine such as sulfur which forms sulfuric acid in the combustion process enters the cylinder. This necessitates the use of a lubricating liquid to protect the inner surface of the cylinder liner from the attack of sulfuric acid, which lubricates the oil with a low pH value on the inner surface of the cylinder liner in order to generally correct for combustion (high pH) use. The cylinder lubrication fluid (oil) is relatively expensive, and the cylinder lubricant used for the cylinder liner inner surface is consumed during engine operation. That is, the new cylinder lubrication liquid must be continuously supplied during engine operation. The consumption of cylinder lubricating liquid is an important factor in the operation of a large low speed two stroke stroke compression ignition internal combustion engine equipped with a crosshead. Therefore, it is necessary to efficiently and accurately lubricate the inner surface of the cylinder liner in order to properly protect the cylinder liner and minimize the consumption of expensive cylinder lubricant.

The injection of the cylinder lubrication liquid is determined not only by the fuel characteristics but also by the engine load and condition. In addition, when treading a new cylinder liner, it is necessary to use about two times the lubrication liquid on the inner surface of the cylinder liner.

The cylinder lubricating oil injection is generally timed to be injected regularly against the rotation of the engine. The injection of the lubricating liquid occurs before or during the passage of the engine piston through the injection quill (injector) during the compression stroke. The injector is evenly distributed around the circumference of the cylinder liner.

One type of device for supplying cylinder lubricating liquid has a plurality of dosing plungers that move in a common drive by a linear actuator. When the linear actuator is activated, the dosing plunger makes the entire stroke and each dosing plunger pumping a predetermined fixed amount of cylinder lubricant to each injector of the cylinder liner. In general, the common drive connecting the dosing plunger to the linear actuator produces a return stroke by the action of a helical spring or other deflection means. In this type of cylinder lubrication apparatus, the dosing plunger can make only the entire stroke and adjustment of the feed rate of the cylinder lubrication liquid to the inner surface of the cylinder liner is achieved by changing the engine revolution speed between the cylinder lubrication events. The highest feed rate is obtained by activating the linear actuator for each engine revolution.

The feed rate should be approximately doubled when taming the new cylinder liners. Therefore, there is a need for a cylinder lubrication apparatus capable of handling up to twice the feed rate required for the engine load of a new cylinder liner from the feed rate required for a low engine load of an already tamed cylinder liner.

A low feed rate is obtained by skipping the injection event for one or more engine revolutions. There may be relatively high dry engine revolutions, especially at low engine loads, where cylinder lubrication liquid injection events do not occur. Ideally, however, the injection should occur for each engine revolution, as there is experience that the dry engine rotation between cylinder lubrication liquid injection may be detrimental to protecting the inner surface of the cylinder liner.

Another type of apparatus for supplying a cylinder lubrication liquid comprises a linear actuator capable of producing a partial stroke of any desired length that is controllable. The injection event of this cylinder lubrication apparatus will typically occur for each engine rotation, with the amount delivered being adjusted by adjusting the stroke length of the linear actuator and accordingly the stroke length of the dosing plunger, exactly matching the current demands of the engine. This type of apparatus for supplying the cylinder lubrication liquid can provide exactly the cylinder lubricant liquid ratio required in all engine operating conditions. However, this type of apparatus for supplying cylinder lubricating liquid is considerably more expensive than the cylinder lubricating apparatus in which the length of the pump stroke is fixed.

WO2008009291 discloses a hydraulic lubrication apparatus for dispensing cylinder lubricant. The dosing system includes a supply line and a return line connected to the lubrication apparatus via one or more respective valves for supplying hydraulic oil, and a central hydraulic pressure supply line connected to the hydraulic cylinder, which is capable of being pressurized by the hydraulic oil through the supply line, An oil supply pump, a plurality of jetting portions and a cylinder lubricating oil supply line connected to respective dosing cylinders having a dosing piston corresponding to a multiple of the number of cylinders in the engine. In order to provide a reliable, inexpensive and risk-free system, even if the hydraulic cylinder fails, the lubrication device is in contact with the dosing piston on one side and on the other side with two or more hydraulic pistons displacing the distribution plate to actuate the dosing piston / RTI >

As a result, it is an object of the present invention to provide an apparatus for supplying a cylinder lubrication liquid which can reduce the demand for an engine rotation event at a low cost without adjusting the cylinder injection event and adjust the supply speed.

It is an object of the present invention to provide a cylinder lubrication apparatus that overcomes or at least reduces the above-mentioned problems in view of this background.

The above and other objects are achieved by the features of the independent claim. Additional implementations are evident from the dependent claims and the detailed description and drawings.

According to the first aspect, there is provided a cylinder liner for supplying a cylinder lubricating liquid to an inner surface of a cylinder liner of a large two-stroke end-stream compression ignition internal combustion engine through a plurality of injectors distributed around the circumference of the cylinder liner, The piston lubricating device comprising: a plurality of piston pumps each having a dosing plunger slidably disposed within a dosing cylinder, a plurality of piston pumps each having a fluid connection to one of the injectors, , A common drive for simultaneously driving all dosing plungers, a hydraulic linear actuator operatively connected to the common drive, and an actuator for driving the common drive during the operation of the cylinder lubrication system Length cylinder lubricator Means for adjusting to a length of at least two predetermined discrete lengths during operation, a first fixed mechanical end stop for determining a first extended position of said common drive, an actuation between said piston and said hydraulic cylinder A drive piston slidably disposed in the hydraulic cylinder having the chamber, a first port disposed at or near the longitudinal end of the hydraulic cylinder, and a second port disposed at a position along the length of the cylinder, spaced from the longitudinal end of the hydraulic cylinder, And a second port connected to the first hydraulic valve.

By providing the means for adjusting the stroke length of the common drive portion to the cylinder lubrication apparatus, it becomes possible to transmit the adjustable amount of the cylinder lubricating liquid to the relatively simple and inexpensive apparatus. By providing the second port at a position along the length of the cylinder at a distance from the longitudinal end of the cylinder in which the first port is located by controlling the opening of the second port with the valve, And may be limited to a position where the drive piston passes through the second port.

According to a first possible embodiment of the first aspect, the apparatus further comprises a second fixed mechanical end stop determining a retracted position of the common drive.

According to a second possible embodiment of the first aspect, the hydraulic linear actuator is a single acting hydraulic linear actuator, and the common driver is biased elastically toward the retracted position.

According to a third possible embodiment of the first aspect, the hydraulic linear actuator is a double acting hydraulic linear actuator.

According to a fourth possible embodiment of the first aspect, the drive piston is provided with a conduit which is open to the working chamber and the cylindrical outer surface of the drive piston.

According to a possible fifth embodiment of the first aspect, the first hydraulic valve is an electronic control valve, and the first electronic control valve is preferably configured to be connected to a hydraulic source or tank in response to a control signal .

According to a possible sixth embodiment of the first aspect, said first port is selectively connected to a pressure source or tank.

According to a possible seventh embodiment of the first aspect, the apparatus further comprises a second hydraulic valve selectively connecting the first port to a pressure source or tank.

According to a possible eighth embodiment of the first aspect, the second hydraulic valve is an electronic control valve configured to connect the first port to a pressure source or tank in response to a control signal.

According to a possible ninth embodiment of the first aspect, the distance between the end of the cylinder and the second port is less than the distance between the second fixed mechanical end stop and the first fixed mechanical end stop.

According to a possible tenth embodiment of the first aspect, the pump stroke of the shorter one of the at least two individual stroke lengths of the common drive is selected when the first hydraulic valve is opened, and at least two individual strokes A pump stroke of longer length is selected when the first hydraulic valve is closed.

According to a possible eleventh embodiment of the first aspect, the apparatus comprises a controller configured to provide a control signal in response to an indication of a human operator or in connection with an engine operating parameter, the control signal connecting the first hydraulic control valve to a hydraulic source or tank, .

According to the second aspect, there is provided a cylinder lubrication apparatus for supplying a cylinder lubrication liquid to an inner surface of a cylinder liner of a large two-stroke end-stream compression ignition internal combustion engine through a plurality of injectors distributed around the circumference of the cylinder liner, Wherein a reciprocating piston forms a cylindrical interior slidably disposed, the cylinder lubrication apparatus comprising: A plurality of piston pumps each having an injection plunger slidably disposed within the dosing cylinder, a respective dosing cylinder including a pump chamber fluidly connected to the pump outlet for fluid connection to one of the injectors, A common drive part for simultaneously driving the plunger, a hydraulic linear actuator operatively connected to the common drive part, and a cylinder lubrication device, during operation of the cylinder lubrication device during operation of the cylinder lubrication device, Wherein the movable mechanical end stop has a first position for forming an end stop for the common driver at a first extended position of the common driver and a second position for forming an end stop for the common driver at the second extended position, Common mechanical end stops Includes; in the second extended position of the first extended position and a drive section of another common East movable mechanical end stop section forming an end stop for the parts of the common driving unit.

According to a first possible embodiment of the second aspect, the apparatus further comprises a second fixed mechanical end stop determining a retracted position of the common driver.

According to a possible second embodiment of the second aspect, the movable mechanical end stop is operatively connected to an actuator of the end stop, and the actuator of the end stop moves the movable mechanical end stop between the first position and the second position .

According to a possible third embodiment of the second aspect, the actuator of the end stop receives the control signal and the actuator of the end stop receives the control signal from the first position to the second position, To the first position.

According to a possible fourth embodiment of the second aspect, the movable end stop includes a rod slidably disposed in the bore, the movable end stop being configured to lock the rod in the first or second position do.

According to a possible fifth embodiment of the second aspect, the second longitudinal end of the rod defines an end stop abutting surface abutting the common drive portion abutment surface of the common drive portion.

According to a possible sixth embodiment of the second aspect, the rod is fixed in a first position by a third fixed mechanical end stop, and the rod is fixed in a second position by a movable bolt.

According to a possible seventh embodiment of the second aspect, the bolt is slidably disposed in the guide passage, and the bolt moves the bolt between a retracted position not protruding from the guide passage and an extended position protruding from the guide passage And is operatively connected to the configured end stop actuator.

According to a possible eighth embodiment of the second aspect, the bolt is disposed between the third fixed mechanical end stop and the rod when the bolt is in the extended position.

According to a possible ninth embodiment of the second aspect, the guide passage is arranged substantially across the axis of the rod.

According to a possible tenth embodiment of the second aspect, the bolt is provided with a beveled tip.

According to a possible eleventh embodiment of the second aspect, the second longitudinal end of the rod opposite the first longitudinal end is provided with an inclined portion.

According to a possible twelfth embodiment of the second aspect, the rod is biased elastically toward the first position.

According to a possible thirteenth embodiment of the second aspect, the end stop actuator is a linear actuator, preferably a single acting linear actuator, but the bolt is resiliently biased towards its retracted position.

According to a possible fourteenth embodiment of the second aspect, the end stop actuator is a linear pneumatic actuator, a linear hydraulic actuator or a linear electric actuator.

According to a fifteenth possible embodiment of the second aspect, the maximum stroke of the common driver between the second fixed mechanical end stop and the movable end stop is such that when the movable end stop is at the first position, 2 position.

These and other aspects of the invention will become apparent from the embodiments described below.

BRIEF DESCRIPTION OF THE DRAWINGS In the following detailed description of the invention, the invention is explained in more detail with reference to the embodiments shown in the drawings.
1 is a front elevational view of a large two-stroke diesel engine according to an embodiment of the present invention.
Fig. 2 is a side elevational view of the large two-stroke engine of Fig. 1; Fig.
Figure 3 is a schematic representation of a large two-stroke engine according to Figure 1;
Fig. 4 is a longitudinal sectional view of a cylinder liner and a cylinder frame of the engine of Figs. 1 to 3; Fig.
5 is a side view of the cylinder liner of Fig.
6 is a cross-sectional view of the cylinder liner of Fig.
7 is an elevational view of an apparatus for supplying a cylinder lubrication liquid according to an exemplary embodiment.
Fig. 8 is a plan view of the cylinder liner of Fig. 7;
9 is a longitudinal sectional view of the apparatus of Fig.
Figure 10 is another longitudinal section view of the Figure 7 apparatus.
11 is a partially enlarged view of Fig.
12 is a longitudinal sectional view of another embodiment of the cylinder lubrication liquid supply apparatus.
13 is another cross-sectional view of the apparatus of Fig.
Figure 14 is an enlarged elevation view of the device bolts of Figure 12;
Figure 15 is a schematic representation of the device of Figure 12;
16 is a schematic representation of an exemplary embodiment of a device for supplying a cylinder lubricating liquid.

In the following detailed description, an apparatus for supplying a cylinder lubrication liquid to the inner surface of a cylinder liner of an internal combustion engine will be described with reference to a large two-stroke low-speed turbo-charged compression ignition internal combustion engine including a crosshead of embodiments.

Figures 1, 2 and 3 illustrate a large low speed turbocharged two stroke compression ignition engine with a crankshaft 8 and a crosshead 9. Figure 3 shows a schematic representation of a large low speed turbocharged two stroke diesel engine with intake and exhaust systems. In this exemplary embodiment, the engine has six cylinders in a row. A large low speed turbocharged two stroke diesel engine is typically supported by a cylinder frame 23 supported by an engine frame 11 and has four to fourteen cylinders in heat. The engine can be used, for example, as a main engine of a ship or as a stationary engine that operates a generator of a power plant. The total output of the engine may range, for example, from 1,000 to 110,000 kW.

The engine is a two-stroke, single-flow type compression ignition engine having, in this embodiment, a scavenge pot 18 in the lower region of the cylinder liner 1 and an exhaust valve 4 in the upper center of the cylinder liner 1 . The scavenge passes from the scavenging accommodating portion 2 to the scavenging port 18 of the individual cylinder 1. The piston 10 in the cylinder 1 compresses the air and the fuel is injected through the fuel injection valves 50 of the cylinder cover 22 so that the combustion proceeds and the exhaust gas is generated.

When the exhaust valve 4 is opened, the exhaust gas flows to the exhaust gas receiving portion 3 through the exhaust duct coupled with the cylinder 1, and then flows through the first exhaust conduit 19 to the turbocharger 5 After flowing into the turbine 6, the exhaust gas is discharged via the second exhaust conduit 7 via the economizer 20 to the outlet 21 and into the atmosphere. The turbine (6) drives the compressor (7) through fresh air through the intake port (12) through the shaft. The compressor (7) transfers the pressurized scoop to the scraper conduit (13) leading to the scoop storage portion (2). The scavenge in the scavenge conduit (13) passes through the intercooler (14) for expected cooling.

If the compressor 7 of the turbocharger 5 does not deliver sufficient pressure to the scavenging receiver 2, that is, in low or partial load conditions of the engine, the scavenging of the electric motor 17, which presses the scavenging flow, Through an auxiliary blower 16 driven by a blower. At a higher engine load, the turbocharger compressor 7 delivers a sufficiently compressed scavenger then the auxiliary blower 16 is bypassed via the check valve 15.

Figures 4, 5 and 6 show a single cylinder liner 1 in longitudinal, side and plan views, respectively. The cylinder cover 22 is fixed on the upper longitudinal end of the cylinder liner 1 by a cylinder cover stud 43 which is tightened with a nut 44 tightened with a hydraulic force. The lower end of the cylinder cover stud 43 is anchored to the cylinder frame 23. The cylinder cover 22 is provided with a central opening 46 for the exhaust valve. The cylinder liner 1 is provided with a plurality of scavenging ports 18 arranged in the vicinity of the lower longitudinal direction. The cylinder liner 1 is carried by the cylinder frame 23 while the shoulder of the cylinder liner 1 is placed on the upper surface of the cylinder frame 23.

The inner surface 25 of the cylinder liner 1 is generally smooth except for a relatively small recess in which the nozzle of the injector 24 injecting the cylinder lubricating liquid is received. The injectors 24 are disposed at substantially the same height and evenly distributed around the circumference of the cylinder liner 1. [

The injectors 24 are inserted into the wall of the cylinder liner 1 and extend from the outside of the cylinder liner 1 into the cylinder liner 1 and the nozzles of the injectors 24 tip are inserted into the above- And is accommodated in the recess. The injectors 24 serve to inject the cylinder lubrication liquid onto the inner surface 25 of the cylinder liner 1. Various techniques are used to ensure that the injected cylinder lubricating liquid ends at the inner surface 25. Some techniques inject the injected cylinder lubrication liquid directly from the nozzle bore into the inner surface 25 before the piston 10 reaches the height at which the injector 24 is disposed during the compression stroke. Another technique allows the cylinder lubrication liquid to be injected accurately between the piston rings of the piston 10 at the instant that the piston 10 is at the height of the injector 24 during the compression stroke. Any type of technique can be used in the present invention to ensure that the cylinder lubrication liquid reaches the inner surface of the cylinder liner 25.

The injector 24 is connected to an apparatus 55 which supplies the cylinder lubrication liquid via respective supply conduits 41.

Figs. 7, 8, 9, 10 and 11 show the first embodiment of the apparatus for supplying the cylinder lubrication liquid to the inner surface 25 in an elevated state, a plan view, a longitudinal sectional view and an enlarged view. The cylinder lubrication apparatus 55 includes a housing 60 that can be assembled into several components in this embodiment but can be formed as a single component.

The cylinder lubrication apparatus 55 includes a pump including a plurality of positive displacement pumps formed by a plurality of dosing plungers 70 slidably disposed in a corresponding dosing cylinder 72. The cylinder lubrication apparatus 55 also includes a linear actuator configured to simultaneously move all the dosing plungers 70 during the pump and intake strokes. The linear actuator is operatively connected to all dosing plungers 70 via a common drive 80.

The linear actuator is a linear hydraulic actuator 83 that includes a drive piston 82 received in a mating cylinder disposed in a housing 60 in the illustrated embodiment. The drive piston (82) forms a drive chamber (81) in the housing (60) together with the mating cylinder. It will be appreciated, however, that the hydraulic actuator 83 may be a component that is completely separate from its own housing.

The drive piston (82) is operatively connected to a common drive (80). In this embodiment, the drive piston and the common driver 80 are a single integral component. It will be appreciated, however, that the common drive 80 and drive piston 82 need only be operatively connected and thus may be separate components.

A helical spring (75) is disposed in the spring chamber (73). The helical spring 75 serves to elastically deflect the common driving portion 80 in the position where the dosing plunger 70 is fully retracted, that is, to make the suction stroke. The common driver 80 is partially disposed in the spring chamber 73.

In this embodiment, the linear actuator is a single acting linear hydraulic actuator 83 configured to power the pump stroke of the dosing plunger 70 through the common drive 80, and the return (intake) of the dosing plunger 70 is a single- The stroke is powered by a helical wire spring 75. The helical wire spring 75 may be replaced by any other suitable resilient means for resiliently tilting the common drive 80 to the retracted position of the dosing plunger 70. [ Or the linear actuator may be a double acting linear actuator that provides power to both the pump and suction strokes of the dosing plunger 70. [

A pump chamber is formed in each dosing cylinder 72. Each pump chamber is connected to a cylinder lubrication inlet chamber 65 through a check valve 62. The cylinder lubrication liquid in the chamber 65 is connected to the cylinder lubricating liquid supply source (not shown) via the cylinder lubrication inlet port 61. When the dosing plunger 70 simultaneously retracts during the intake stroke, the pump chamber communicates with the cylinder lubrication liquid inlet port 61, the cylinder lubrication liquid inlet chamber 65, and the respective counter- The cylinder lubrication liquid is recharged. Each pump chamber is connected to the outlet port 62 via passage 77. Each outlet port 62 is connected to the injector 24 via a supply conduit 41. The volume of the pump chamber is the smallest when the dosing plunger 70 most extends into the dosing cylinder and is largest when the dosing plunger 70 retracts most from the dosing cylinder.

As the dosing plunger 70 simultaneously moves into the dosing cylinder 72 during the pump stroke, the cylinder lubrication liquid in the pump chamber flows through the respective passageway 77, each outlet port 62, each supply conduit 41, And is pushed out to each of the injectors 24. That is, each dosing plunger 70 is connected to a single injector 24 in one embodiment.

The hydraulic linear actuator 83 includes a drive piston 82 slidably disposed in the mating cylinder with a drive chamber 81 between the drive piston 82 and the mating cylinder. The first port 84 is disposed at or near the longitudinal end of the mating cylinder and the second port 86 is disposed at a position along the length of the mating cylinder at a distance from the longitudinal end of the mating cylinder. The second port 86 is in the form of a ring chamber or annular groove in one embodiment.

At the longitudinal end of the drive piston 82 towards the actuation chamber 81 is provided a conduit connecting the actuation chamber 81 to the circumferential outer surface of the drive piston 82, as best shown in the enlarged cross-sectional view (C) do. This conduit is formed by a longitudinal channel 89 which in this embodiment is connected to one or more radial channels 88 that open to the drive chamber 81 and open to the cylindrical outer surface of the drive piston 82.

The first port 84 is connected to the second hydraulic valve 59 via the passage 85. The second hydraulic pressure valve 59 selectively connects the first port 84 to the pressure source or the tank. When the second hydraulic valve 59 connects the first port 84 to the pressure source, the operation chamber 81 is pressurized and the drive piston 82 applies force to the common drive 80 in the pump stroke direction, A force is applied to the plunger 70 to make a pump stroke. The pump stroke is mechanically limited by the first mechanical end stop in this example embodiment formed by the first abutment surface 36 of the common drive abutting the second abutment surface 37 of the housing 60. [ Thus, the first mechanical end stop determines the maximum extension position of the dosing plunger 70.

When the second hydraulic valve 59 connects the first port 84 to the tank, the drive piston 82 does not exert a considerable force on the common drive unit 80, so that the helical spring 70 retracts the dosing plunger 70 Push back into position to create an inhalation stroke. The helical spring 70 causes the common driver 80 to move in the suction stroke direction until the third abutment surface 38 of the common driver 80 abuts against the fourth surface 35 of the housing 60, Thereby forming a second fixed mechanical end stop for the most retracted position of the dosing plunger 70.

The second port 86 is connected to the tank via the bleed conduit 87 and the first hydraulic valve 58. When the first hydraulic valve 58 is in the first position, it connects the second port 86 to the tank via the bleed conduit 87. When the radial channel 88 of the actuating piston 82 reaches the second port 86 when the first hydraulic valve 58 is in the second position during the pump stroke, the drive chamber 81 is connected to the tank . That is, the radial channel faces the second port 86, thereby depressurizing the drive chamber 81 and terminating the pump stroke. The second port 86 thus forms part of the hydraulic end stop which limits the pump stroke to the short length L1 by connecting the operating chamber 81 to the tank when a short stroke length L1 is achieved.

When the first hydraulic valve 58 is connected to the hydraulic source during the pump stroke, the actuating piston 82 makes the entire stroke of the length L2. That is, the pump stroke continues until the abutment surface 36 of the common drive abuts the second abutment surface 37 (first stationary mechanical end stop) of the housing 60.

The length of the entire stroke L2 is longer than the length of the short stroke L1. The distance between the longitudinal end of the mating cylinder in which the first port 84 is located and the second port 86 position determines the length of the short stroke L1 with the position of the radial channel 88. It can be seen that the conduits and radial passages 88 formed by the axial passageways 89 are unnecessary. Without this conduit, however, the second port 86 needs to be placed closer to the first port 84 to obtain the same short stroke length L1.

The pump stroke is initiated by moving the second hydraulic valve 59 to a position connected to the source of fluid pressure and the pump stroke is terminated by moving the second hydraulic valve 59 to a position connected to the tank. The length of the pump stroke is determined by the position of the first hydraulic valve 58. A long pump stroke of length L2 is obtained when the first hydraulic valve 58 is connected to a source of fluid pressure and a short stroke of L1 length is obtained when the first hydraulic valve 58 is connected to the tank. In one embodiment, the first hydraulic valve 58 is an electronic control valve, such as a solenoid valve, that receives control signals. In one embodiment, the second hydraulic valve 59 is an electronic control valve, such as a solenoid valve, that receives control signals.

In another embodiment (not shown), the first control valve 58 is a simple valve that can be opened or closed, and a valve in the open position connects the second port 86 to the tank. In this embodiment, the short stroke length L1 is obtained by opening the first hydraulic valve 85, and the long stroke length L2 is obtained by closing the first hydraulic valve 85. [

12, 13, 14, and 15 are longitudinal sectional views and detailed and schematic views showing another embodiment of the cylinder lubricating liquid supply apparatus 55, respectively. The cylinder lubrication apparatus 55 of the embodiment of Figs. 12 to 15 is substantially the same as the cylinder lubrication apparatus 55 of Figs. 7 to 11, and the same reference numerals denote the same features, but the following differences exist.

The linear actuator 83 is not provided with a second port or a bleed channel. The drive piston 81 is not provided with a conduit connecting the drive chamber 81 to the cylindrical outer surface of the drive piston 81 and has no first hydraulic valve.

The second hydraulic valve 59 selectively connects the drive chamber 84 to a hydraulic source or tank. Without the second bore 86, the stroke length of the dosing plunger 70 can not be limited to the short length L 1 by reducing the pressure in the operation chamber 81. Instead, the short stroke length L1 is limited by the movable mechanical end stops in this exemplary embodiment. The movable mechanical end stop has at least two positions. Fig. 12 shows the position of the movable mechanical end stop resulting in a short stroke of L1 length, and Fig. 13 shows the position of the movable mechanical end stop resulting in a long stroke of L2 length.

The movement of the dosing plunger 70 in the suction stroke direction causes the second fixed mechanical end stop 38, which is formed by abutting the third abutment surface 38 of the common drive portion 80 against the fourth abutment surface 35 of the housing 60, To form a second stationary mechanical end stop for the most retracted position of the dosing plunger 70. As shown in FIG. The positions where the dosing plunger 70 and the common driver 80 are retracted are shown in Figs. 12 and 13. Fig.

The movable mechanical end stop includes an end stop actuator operatively connected to the movable mechanical end stop.

The actuator of the end stop is configured to move the movable mechanical end stop between the first position and the second position.

The actuator of the end stop part receives a control signal from the electronic control unit 100 and the actuator of the end stop part moves the mechanical end stop from the first position to the second position upon receiving the control signal from the electronic control unit 100 And is configured to move from the second position to the first position. Alternatively, the position of the mechanical end stop can be easily controlled by the operator using a control button that sends a signal to the end stop actuator.

The movable end stop includes a rod 94 slidably disposed within the matching bore. The rod 94 may be held in the first or second position by an end stop actuator.

The first longitudinal end of the rod 94 forms a second abutment surface that abuts the first abutment surface 36 of the common drive 80.

The rod 94 is fixed in the first position by the third fixed mechanical end stop and the rod 94 is fixed in the second position by the bolt.

The third fixed mechanical end stop is formed by a plug (93). The plug 93 is fixed to the bore of the housing 60. The plug 93 may be threaded to thread with the threaded bore of the housing 60 and the position of the plug 93 is adjusted by the rotation of the plug 93 in this case. The plug 93 is disposed on the same axis as the common drive portion 80 and has a fifth adjoining surface 28 facing in the axial direction. The rod 94 is provided in the longitudinal direction and faces the axially facing sixth abutment surface 29 with the plug 93. 13 when the bolt 90 is in the position shown in Fig. 13, the rod 94 is moved until the sixth abutment surface 29 of the rod 94 abuts against the fifth abutment surface 28 of the plug 93, It can be continuously moved in the direction of the stroke. This is the first position of the mechanical end stop allowing a pump stroke of longer length L2. In this position, the bolt 90 is in the retracted position, which is not extended between the rod 94 and the plug 93.

The bolt 90 is slidably disposed in a guide passage that is substantially perpendicular to the axis of the rod 94. The bolt 93 is configured to move the bolt 93 between a retracted position that does not protrude from the guide passage as shown in Figure 13 and an extended position that protrudes between the rod 94 and the plug 93 from the guide passage, Is operatively connected to the stationary actuator, thereby pushing the rod 94 into the second position. This is the second position of the mechanical end stop providing a pump stroke with a short length L1.

In this embodiment the bolt 93 is provided with a sloped tip 97 and a sloped portion 33 is provided at a second longitudinal end opposite the first longitudinal end of the rod 94. When the end stop actuator moves the bolt 93 from the retracted position to the extended position, the tapered tip 97 engages the tapered portion 33 to create a force having an axial component on the rod 94 15 to force the rod 94 to the second position as shown by the intermittent line. In the second position, the second abutment surface 37 is closer to the second stationary mechanical end stop, so that the pump stroke is such that the bolt 90 is in the extended position forcing the rod 94 to the second position And has a short length L1.

In an embodiment, the rod 94 is resiliently biased towards the first position.

When the bolt 90 is in the retracted position, the rod is in the first position and the pump stroke has a longer length L2.

The end stop actuator is a linear actuator operatively connected to the bolt (90). The end stop actuator is a single acting linear actuator in which in one embodiment the bolt 90 is elastically biased to its retracted position. It will be appreciated that the end stop actuators in this embodiment are linear pneumatic actuators, but the end stop actuators may be linear hydraulic actuators, linear electric actuators or passive actuators.

The linear pneumatic actuator has a longitudinal end of a bolt 90 opposing an inclined tip 97 provided with a head 91 which acts as a piston slidably and sealingly disposed in a pneumatic cylinder 95 And a pneumatic cylinder 95. The pneumatic cylinder 95 is connected to the pneumatic valve 99 via a pneumatic conduit 96. The pneumatic valve 99 is a solenoid valve connected to the electronic control unit 100 in one embodiment. Pneumatic valve 99 is configured to connect pneumatic conduit 96 to a pneumatic source or atmosphere.

The pneumatic valve 99 connects the pneumatic conduit 96 to the pneumatic pressure source, if the electronic control unit 100 signals to select the short stroke of the dosing plunger 70 at length L2. The resulting pressure acting on the head 91 forces the bolt 90 to the extended position, as shown in Figure 12, thereby causing the rod 94 to move to the second position. The pneumatic valve 99 connects the pneumatic conduit 96 to the atmosphere as long as the electronic control unit 100 gives a signal to select the short stroke of the dosing plunger 70 at length L1. The resultant lack of pressure action associated with the elastic deflection on the bolt 90 forces the bolt 90 to its retracted position, as shown in Figure 13, .

16 is a schematic view of a third embodiment of an apparatus 55 for supplying a cylinder lubrication liquid to the inner surface 25 of the cylinder liner. The apparatus 55 according to this embodiment is similar to the apparatus 55 of Figures 12-15 except that the bolts 90 are replaced by hydraulic wedges and the pneumatic valves are replaced by third hydraulic valves 99 ' Essentially the same. In this embodiment, a portion of the rod 94 acts as a piston in the bore in which the rod 94 is received. Accordingly, a hydraulic chamber 30 is formed between the rod 94 and the plug 93. [ The hydraulic chamber 30 is connected to the third hydraulic valve 99 'via a hydraulic conduit 96'. The third hydraulic valve 99 is an electronic control valve connected to the electronic control unit 100 in one embodiment. The electronic control valve 99 'is configured to connect the hydraulic conduit 96' to a hydraulic source or tank upon receipt of each command from the electronic control unit 100. When the third hydraulic valve 99 'connects the hydraulic conduit 96' to the hydraulic source, the pressure in the hydraulic chamber 30 increases and causes the rod 94 to move to the second position indicated by the intermittent line, Causing the pump stroke for the plunger 70 to be selected to a shorter length. When the third hydraulic valve 99 'connects the hydraulic conduit 96' to the tank, the lack of pressure in the hydraulic chamber 30 causes the rod 94 to move to the first position, Have the administration choose a longer length.

The apparatus 55 for supplying the cylinder lubrication liquid to the inner surface 25 of the cylinder liner 1 having at least two different lengths for the pump stroke can be used in various ways. One method of using the device 55 is to use a long pump stroke of L2 length for injection for each engine rotation when tilting the new cylinder liner 1, To deliver the maximum feed rate for normal operation using a short pump stroke of L1 length. The injection is skipped when the engine is running at low loads, but it is significantly more frequent compared to prior art devices where the length is single fixed with respect to the pump stroke.

Although the above embodiments have described the automatic control of the stroke length using the electronic control device, the stroke length of the dosing plunger 70 pump stroke can be controlled manually by manually controlling each hydraulic or pneumatic valve, , It can be seen that it is possible to control by pressing a button.

The term " comprising "used in the claims does not exclude other elements or steps. The term "a" as used in the claims does not exclude a plurality. The electronic control device can perform the functions of various means described in the claims. Reference signs used in the claims shall not be construed as limiting the scope. Although the present invention has been described in detail for the purpose of illustration, it is to be understood that such detail is solely for that purpose and may be modified by those skilled in the art without departing from the scope of the present invention.

Claims (28)

Cylinder lubricating device 55 for supplying the cylinder lubrication liquid to the inner surface 25 of the cylinder liner 1 of the large two-stroke end-stream compression ignition internal combustion engine via a plurality of injectors 24 distributed around the circumference of the cylinder liner , Said cylinder liner (1) defining a cylindrical interior in which a reciprocating piston (10) is slidably disposed, said cylinder liner (1)
A plurality of piston pumps each having an injection plunger 70 slidably disposed within a dosing cylinder 71 and each dosing cylinder 71 having a fluid connection to one of the injectors 24 A plurality of piston pumps including a pump chamber (72) fluidly connected to the pump outlet (62);
A common drive unit 80 for simultaneously driving all the dosing plungers 70;
A hydraulic linear actuator 83 operatively connected to the common driver 80; And
Means for adjusting the stroke length of the common drive unit 80 during operation of the cylinder lubrication apparatus 55 to any one of at least two predetermined lengths L1 and L2 during operation of the cylinder lubrication apparatus In addition,
The first fixed mechanical end stop determines the first extended position of the common driver 80,
The hydraulic linear actuator 83 includes a drive piston 82 slidably disposed in the mating cylinder having an operation chamber 81 between the drive piston 82 and the mating cylinder, And a second port (86) disposed at a position along the length of the mating cylinder and spaced from a longitudinal end of the mating cylinder and connected to a first hydraulic valve (58). The first port (84) (55). ≪ / RTI > The cylinder lubrication apparatus (55) according to claim 1, further comprising a second fixed mechanical end stop (52) for determining a retracted position of the common driver (80). The cylinder lubrication apparatus (55) according to claim 1 or 2, wherein the hydraulic linear actuator (83) is a single-acting hydraulic linear actuator, and the common drive (80) is resiliently biased toward a retracted position. The cylinder lubrication apparatus (55) according to any one of claims 1 to 3, wherein the hydraulic linear actuator (83) is a double acting hydraulic linear actuator. The apparatus according to any one of claims 1 to 4, wherein the drive piston (82) is provided with conduits (88, 89) that open to the cylindrical outer surface of the operation chamber (81) and the drive piston (55). 7. The control valve according to claim 6, wherein the first hydraulic valve (58) is an electromagnetic control valve, and the first electromagnetic control valve is preferably configured to take an open position or a closed position in response to a control signal Device (55). The cylinder lubrication apparatus (55) according to any one of claims 1 to 6, wherein the first port (84) is selectively connected to a pressure source or a tank. The cylinder lubrication apparatus (55) according to claim 7, comprising a second hydraulic valve (59) selectively connecting the first port (84) to a pressure source or a tank. The cylinder lubrication apparatus (55) according to claim 8, wherein the second hydraulic valve (59) is an electronic control valve configured to connect the first port (84) to a pressure source or a tank in response to a control signal. 10. A method according to any one of claims 1 to 9, wherein the distance between the end of the cylinder and the second port (86) is smaller than the distance between the second fixed mechanical end stop and the first fixed mechanical end maintenance Characterized by a cylinder lubrication device (55). A pump stroke according to any one of claims 9 and 10, wherein the shorter one of the at least two individual stroke lengths of the common drive (80) is selected when the first hydraulic valve (58) is in the first position , And the pump stroke of the longer one of the at least two individual stroke lengths of the common drive (80) is selected when the first hydraulic valve is at another position. The cylinder lubrication apparatus according to claim 11, further comprising a controller configured to change a position in response to an instruction from a human operator or in response to an engine operating parameter by signaling the first hydraulic control valve (58) (55). A cylinder lubrication apparatus 55 for supplying cylinder lubricating liquid to the inner surface 25 of the cylinder liner 1 of the large two-stroke upstream-stage compression ignition internal combustion engine via a plurality of injectors 24 distributed around the circumference of the cylinder liner 1, , Said cylinder liner (1) forming a cylindrical interior in which a reciprocating piston (10) is slidably disposed, said cylinder liner (1)
A plurality of piston pumps each having an injection plunger 70 slidably disposed within a dosing cylinder 71 and each dosing cylinder 71 having a fluid connection to one of the injectors 24 A plurality of piston pumps including a pump chamber (72) fluidly connected to the pump outlet (62);
A common drive unit 80 for simultaneously driving all the dosing plungers 70;
A hydraulic linear actuator 83 operatively connected to the common driver 80; And means for adjusting the stroke length of the common drive portion (80) during operation of the cylinder lubrication device (55) to the length of any one of at least two predetermined individual lengths (L1, L2) during operation of the cylinder lubrication apparatus In addition,
Wherein the movable mechanical end stop has a first position in which it forms an end stop with respect to the common driver (80) at a first extended position of the common driver (80) and a second position at which the second mechanical extension , The movable mechanical end stop is moved from the first extended position of the common driving unit (80) to the second extended position of the common driving unit (80) at a second position forming an end maintenance unit for the common driving unit (55). 14. The cylinder lubrication apparatus (55) according to claim 13, further comprising a second fixed mechanical end stop portion for determining a retreat position of the common drive portion (80). 14. A method according to claim 13 or claim 14, wherein the movable mechanical end stop is operatively connected to an actuator of the end stop, and the actuator of the end stop is configured to move the movable mechanical end stop between the first position and the second position Characterized by a cylinder lubrication device (55). 16. The actuator of claim 15, wherein the actuator of the end stop receives the control signal and receives the control signal, the actuator of the end stop moves the mechanical end stop from the first position to the second position or from the second position to the first position (55). ≪ / RTI > 16. A device according to any one of claims 13 to 16, wherein the movable end stop includes a rod (94) slidably disposed in the bore, the movable end stop defining the rod (94) in a first or second position To the cylinder lubrication apparatus (55). A cylinder lubrication system according to claim 17, wherein the first longitudinal end of the rod (94) forms an end stop adjacent surface (37) abutting the common drive side abutment surface (36) of the common drive Device (55). A device according to claim 17 or 18, wherein the rod (94) is fixed in the first position by a third fixed mechanical end stop (93) and the rod (94) is fixed by the movable bolt (55). ≪ / RTI > The bolt (90) according to claim 19, wherein the bolt (90) is slidably disposed in the guide passage and the bolt (90) is in a retracted position in which the bolt (90) And is operatively connected to an end stop actuator configured to move the bolt (90) between the protruding extended positions. The cylinder lubrication apparatus of claim 20, wherein the bolt (90) is disposed between the third fixed mechanical end stop (93) and the rod (94) when the bolt (90) (55). The cylinder lubrication apparatus (55) according to any one of claims 17 to 21, characterized in that the guide passage is arranged substantially across the axis of the rod (94). The cylinder lubrication apparatus (55) according to any one of claims 19 to 22, characterized in that the bolt (90) is provided with an inclined tip. A cylinder lubrication apparatus according to claim 22, characterized in that a sloped portion (33) is provided at a second longitudinal end of the rod (94) opposite the first longitudinal end of the rod (94) ). The cylinder lubrication apparatus (55) according to any one of claims 17 to 24, characterized in that the rod (94) is resiliently oriented in a first position. 26. A cylinder according to any one of claims 15 to 25, characterized in that said end stop actuator is a linear actuator, preferably a single acting linear actuator, said bolt (90) being resiliently biased towards its retracted position Lubricating device (55). The cylinder lubrication apparatus (55) according to claim 26, wherein the end stop actuator is a linear pneumatic actuator, a linear hydraulic actuator or a linear electric actuator. 28. A method according to any one of claims 13 to 27, wherein the maximum stroke of the common driver between the second fixed mechanical end stop and the movable end stop is such that when the movable end stop is at the first position, 2 position. The cylinder lubrication apparatus 55 according to claim 1,

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