• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
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  • 优先权
    • 专利摘要:
    A large slow-running two-stroke engine and a method of lubricating the engine with an injector (4) that comprises an electrically driven inlet valve system (13). Optionally, for the inlet valve system, a valve is provided in which a reciprocal member (25) is provided inside a bushing (24) of a stationary valve member (23). The stationary valve member (23) comprises a transverse canal (28) extending transversely through the bushing (24) and which is closed by the reciprocal member (25) in an idle phase and which is only opened when a throughput section (25A) of the reciprocal member (25) gets aligned with the transverse canal (28) for the injection phase. When the transverse canal (28) is opened, a lubricant inlet port (12) of the injector (4) communicates with a nozzle aperture (5’) of the injector (4), and lubricant is injected into the cylinder (1) of the engine.
    公开号:DK201770940A1
    申请号:DKP201770940
    申请日:2017-12-13
    公开日:2019-09-06
    发明作者:Bak Peer
    申请人:Hans Jensen Lubricators A/S；
    IPC主号:
    专利说明:

    Large slow-running two-stroke engine and method of lubricating such engine, as well as an injector for such engine and method and a valve system
    FIELD OF THE INVENTION
    The present invention relates to a large slow-running two-stroke engine and a method of lubricating such engine, as well as an injector for such engine and method and a valve system.
    BACKGROUND OF THE INVENTION
    Due to the focus of on environmental protection, efforts are on-going with respect reduction of emissions from marine engines. This also involves the steady optimization of lubrication systems for such engines, especially due to increased competition. One of the economic aspects with increased attention is a reduction of oil consumption, not only because of environmental protection but also because this is a significant part of the operational costs of ships. A further concern is proper lubrication despite reduced lubricant volume because the longevity of diesel engines should not be compromised by the reduction of oil consumption. Thus, there is a need for steady improvements with respect to lubrication.
    For lubricating of large slow-running two-stroke marine diesel engines, several different systems exist, including injection of lubrication oil directly onto the cylinder liner or injection of oil quills to the piston rings.
    An example of a lubricant injector for a marine engine is disclosed in EP1767751, in which a non-retum valve is used to provide the lubricant access to the nozzle passage inside the cylinder liner. The non-return valve comprises a reciprocating springpressed ball in a valve seat just upstream of the nozzle passage, where the ball is displaced by pressurised lubricant. The ball valve is a traditional technical solution,
    DK 2017 70940 A1 based on a principle dating back to the start of the previous century, for example as disclosed in GB214922 from 1923.
    An alternative and relatively new lubrication method, compared to traditional lubrication, is commercially called Swirl Injection Principle (SIP). It is based on injection of a spray of atomized droplets of lubricant into the scavenging air swirl inside the cylinder. The helically upwards directed swirl results in the lubricant being pulled towards the Top Dead Centre (TDC) of the cylinder and pressed outwards against the cylinder wall as a thin and even layer. This is explained in detail in international patent applications W02010/149162 and W02016/173601. The injectors comprise an injector housing inside which a reciprocating valve member is provided, typically a valve needle. The valve member, for example with a needle tip, closes and opens the lubricant’s access to a nozzle aperture according to a precise timing. In current SIP systems, a spray with atomized droplets is achieved at a pressure of, typically, 35-40 bars, which is substantially higher than the oil pressure of less than 10 bars that are used for systems working with compact oil jets that are introduced into the cylinder. In some types of SIP valves, the high pressure of the lubricant is also used to move a spring-loaded valve member against the spring force away from the nozzle aperture such that the highly pressurised oil is released therefrom as atomized droplets. The ejection of oil leads to a lowering of the pressure of the oil on the valve member, resulting in the valve member returning to its origin and remaining there until the next lubricant cycle where highly pressurized lubricant is supplied to the lubricant injector again.
    In such large marine engines, a number of injectors are arranged in a circle around the cylinder, and each injector comprises one or more nozzle apertures at the tip for delivering lubricant jets or sprays into the cylinder from each injector. Examples of SIP lubricant injector systems in marine engines are disclosed in international patent applications W02002/35068, W02004/038189, W02005/124112, W02010/149162, WO2012/126480, WO2012/126473, WO2014/048438, and W02016/173601.
    For SIP injection, a precisely controlled timing is essential in addition to the objective of minimizing oil consumption. For this reason, SIP systems are specially designed for quick reactive response during injection cycles.
    DK 2017 70940 A1
    However, despite these apparent advantages of SIP lubrication systems and advanced dosing systems for injectors in general, a steady motivation for improvements exists.
    DESCRIPTION / SUMMARY OF THE INVENTION
    It is therefore the objective of the invention to provide an improvement in the art. A particular objective is to provide a better speed and volume control of lubricant ejection by the injector. Especially, it is the objective to improve lubrication with SIP injectors in a large slow-running two-stroke engine. These objectives are achieved by a large slow-running two-stroke engine, a method for lubricating such an engine, an injector for such engine and method, as well as a valve system for the injector as set forth in the following.
    The large slow-running two-stroke engine comprises a cylinder with a reciprocal piston inside and with a plurality of injectors distributed along a perimeter of the cylinder for injection of lubricant into the cylinder at various positions on the perimeter during injection phases. For example, the large slow-running two-stroke engine is a marine engine or a large engine in power plants. Typically, the engine is burning diesel or gas fuel.
    The engine further comprises a controller. The controller is configured for controlling the amount and timing of the lubricant injection by the injectors during an injection phase. Optionally, also the injection frequency is controlled by the controller. For precise injection, it is an advantage if the controller is electronically connected to a computer or comprises a computer, where the computer is monitoring parameters for the actual state and motion of the engine. Such parameters are useful for the control of optimized injection. Optionally, the controller is provided as an add-on system for upgrade of already existing engines. A further advantageous option is a connection of the controller to a Human Machine Interface (HMI) which comprises a display for surveillance and input panel for adjustment and/or programming of parameters for injection profiles and optionally the state of the engine. Electronic connections are optionally wired or wireless or a combination thereof.
    DK 2017 70940 A1
    The term “injector” is used for an injection valve system comprising a housing with a lubricant inlet and one single injection nozzle with a nozzle aperture as a lubricant outlet and with a movable member inside the housing, which opens and closes access for the lubricant to the nozzle aperture. Although, the injector has a single nozzle that extends into the cylinder through the cylinder wall, when the injector is properly mounted, the nozzle itself, optionally, has more than a single aperture. For example, nozzles with multiple apertures are disclosed in WO2012/126480.
    The term “injection phase” is used for the time during which lubricant is injected into the cylinder by an injector. The term “idle phase” is used for the time between injection phases. The term “injection-cycle” is used for the time it takes to start an injection sequence and until the next injection sequence starts. For example, the injection sequence comprises a single injection, in which case the injection-cycle is measured from the start of the injection phase to the start of the next injection phase. The term “timing” of the injection is used for the adjustment of the start of the injection phase by the injector relatively to a specific position of the piston inside the cylinder. The term “frequency” of the injection is used for the number of repeated injections by an injector per revolution of the engine. If the frequency is unity, there is one injection per revolution. If the frequency is 1/2, there is one injection per every two revolutions. This terminology is in line with the above mentioned prior art.
    In a practical embodiment, the housing of the injector comprises a base with a lubricant inlet port for receiving lubricant and comprises a flow chamber, typically a rigid cylindrical flow chamber, which rigidly connects the base with the nozzle. The flow chamber is hollow and, thus, allows lubricant to flow inside the flow chamber from the base to the nozzle. When the injector is mounted, the flow chamber extends through the cylinder wall of the engine so that the nozzle is held rigidly inside the cylinder by the flow chamber. Due to the base being provided at the opposite end of the flow chamber, it is typically located on or at the outer side of the cylinder wall. For example, the injector comprises a flange at the base for mounting onto the outer cylinder wall.
    DK 2017 70940 A1
    In order to fully understand the invention, it is pointed out that it has been discovered that lubricant conduits of a substantial length from a pumping system to the cylinder with the plurality of injectors introduce imprecision of the system. Long conduits tend to expand and retract slightly when being exposed to highly pressurised lubricant, which leads to slight uncertainties in timing and volume of injected lubricant. Furthermore, the lubricant is subject to minute compression and expansion during an injection cycle, which adds to the effect. Although, this effect is small, it introduces errors in the range of milliseconds for the injection, which is substantial in comparison to the short SIP injection time, which can be as little as 10 milliseconds or even below 1 millisecond. Such effect of imprecise timing has substantial influence on SIP lubrication systems due to the high lubricant pressure and the short injection periods. Also, it is noticed that the injection amount is typically regulated by the time length in which pressurised oil is supplied to the nozzle in an injection cycle, in which case, uncertainty factors that affect a precise timing should be minimised, if not eliminated. Improvement with respect to the injection is achieved with a system and method as described in the following with various embodiments and details.
    For sake of convenience, the term “forward motion” is used for motion towards the nozzle aperture and the oppositely directed motion away from the nozzle aperture is called “rearward motion”.
    Each injector comprises a lubricant inlet port for receiving lubricant from a lubricant feed conduit. Typically, the lubricant feed conduit is connected to a common lubricant supply system including a potential lubricant pump that raises the pressure of the lubricant to an adequate level. For the described system, it suffices to provide a constant lubricant pressure at the lubricant inlet port of the injector.
    Each of the injectors comprises an outlet-valve system at the nozzle configured for opening for flow of lubricant to the nozzle aperture during an injection phase upon pressure rise above a predetermined limit at the outlet-valve system and for closing the outlet-valve system after the injection phase. The outlet-valve system closes off for back-pressure from the cylinder and also prevents lubricant to enter the cylinder unless the inlet-valve is open. In addition, the outlet-valve system assists in a short
    DK 2017 70940 A1 closing time after injection, adding to precision in timing and volume of injected lubricant
    For example, the outlet-valve system comprises an outlet non-return valve. In the outlet non-return valve, the outlet-valve member, for example a ball, ellipsoid, plate, or cylinder, is pre-stressed against an outlet-valve seat by an outlet-valve spring. Upon provision of pressurised lubricant in a flow chamber upstream of the outlet-valve system, the pre-stressed force of the spring is counteracted by the lubricant pressure, and if the pressure is higher than the spring force, the outlet-valve member is displaced from its outlet-valve seat, and the outlet non-return valve opens for injection of lubricant through the nozzle aperture into the cylinder. For example, the outlet-valve spring acts on the valve member in a direction away from the nozzle aperture, although, an opposite movement is also possible.
    In contrast to the above-mentioned WO2008/141650 and DE 102013104822, disclosing dosing remotely from the injectors, which leads to such imprecisions, the invention uses a different approach. In order to solve the problem and achieve the objective of providing a better speed and volume control of lubricant ejection by the injector, each of the injectors comprises an electrically-driven inlet-valve system electrically connected to the controller and arranged between the lubricant inlet port and the nozzle for regulating the lubricant that is dispensed through the nozzle aperture by opening or closing for lubricant flow from the lubricant inlet port to the nozzle in dependence of an electrical control-signal received from the controller. The inlet-valve system is arranged upstream of and remotely from the nozzle, and it is also arranged upstream of and remotely from the outlet-valve system.
    For lubricating the engine, the method comprises sending an electrical control signal from the controller to the electrically-driven inlet-valve system and by the control signal causing the inlet-valve system to open for flow of lubricant from the lubricant feed conduit through the lubricant inlet port, through the inlet-valve system, and into a conduit that flow-connects the inlet-valve system with the outlet-valve system. The lubricant flow into the conduit causes a pressure rise at the outlet-valve system, causing the outlet-valve system to open for flow of lubricant from the conduit to the nozzle
    DK 2017 70940 A1 aperture by which lubricant is injected into the cylinder through the nozzle aperture. At the end of the lubrication period, the electrical control signal from the controller is changed, causing the inlet-valve system to close again for lubricant supply from the lubricant inlet port to the nozzle aperture. The pressure in the conduit decreases again, and the outlet valve closes.
    Thus, there are two valve systems in the injector. The inlet-valve system is regulated by electrical signals from the controller and the outlet-valve system is activated only by the elevated pressure of the lubricant at the outlet-valve system for example nonreturn valve, once the inlet-valve system has caused flow of lubricant to the outlet non-return valve. There is no mechanical connection that couples the movable parts of the inlet-valve system with the movable parts of the outlet-valve system. Coupling between the opening and closing of these two systems is done only by the lubricant that flows from the inlet-valve system to the outlet-valve system.
    The inlet-valve system of the injector doses the amount of lubricant for injection by the time the inlet-valve system stays open for the injection phase. The time is determined by the controller.
    Optionally, volume meters can be employed either for the total consumption of all the injectors on a cylinder or for a subgroup of injectors during the injection phase.
    For example, for lubricating the engine, the method comprises sending an electrical control signal from the controller to the electrically-driven inlet-valve system and by the control signal causing the inlet-valve system to open for flow of lubricant from the lubricant feed conduit through the lubricant inlet port, through the inlet-valve system, and into a conduit that flow-connects the inlet-valve system with the outlet-valve system. The lubricant flow into the conduit causes a pressure rise at the outlet-valve system, causing the outlet-valve system to open for flow of lubricant from the conduit to the nozzle aperture and injecting lubricant into the cylinder through the nozzle aperture. At the end of the lubrication period, the electrical control signal from the controller is changed, causing the inlet-valve system to close again for lubricant supply from
    DK 2017 70940 A1 the lubricant inlet port to the nozzle aperture. The pressure in the conduit falls gain, and the outlet valve closes.
    In practical embodiments, the injector comprises an inlet valve system and/or an outlet valve system which is characterized by the following construction. A reciprocal member is provided inside a bushing of a stationary valve member. The valve member comprises a transverse canal extending transversely through the bushing which is closed by the reciprocal member in an idle phase and which is only opened when a throughput section of the reciprocal member gets aligned with the transverse canal for the injection phase. When the transverse canal is opened, a lubricant inlet port of the injector communicates with a nozzle aperture of the injector, and lubricant is injected into the cylinder of the engine.
    The specific valve system is acting fast due to its light-weight components, especially the reciprocal member that is opening and closing for the lubricant flow. Furthermore, the components are relatively simple in construction and imply low production costs. In addition to these advantages, the valve system is reliable, robust, and has a low risk for clogging. As the components are subject to relatively small pressure load, the valve system also has a long lifetime.
    In practical embodiments, the inlet valve system or the outlet valve system or both comprises a valve system as explained in more detail in the following.
    Such valve system comprises stationary valve member, which in turn comprises a cylindrical bushing inside which a cylindrical reciprocal member is provided with a cylinder axis equal to a cylinder axis of the bushing and reciprocally movable inside the bushing along the cylinder axis between a first position and a second position. The term cylindrical bushing is used for describing that the bushing has a cylindrical hollow. The cylindrical reciprocal member fits tightly into the cylindrical hollow of the bushing so that no lubricant can flow between the cylindrical reciprocal member and the cylindrical bushing. A transverse canal extends through the stationary valve member and through the bushing. The transverse canal has a first transverse canal section on one side of the bushing and a second transverse canal section on another side of the
    DK 2017 70940 A1 bushing. The reciprocal member comprises a transverse throughput section for flow of the liquid through the reciprocal member transversely to the cylinder axis. The throughput section of the reciprocal member is arranged for being remote from the transverse canal in the first position for closing the transverse canal and the throughput section of the reciprocal member is arranged for being aligned with the transverse canal only in the second position for flow from the first transverse canal section through the throughput section to the second transverse canal section. In some practical embodiments, the reciprocal member is pre-stressed towards the first position by a spring.
    Optionally, the throughput section is provided as a narrowing section for flow of lubricant from the first transverse canal section around the narrowing section in the bushing and into the second transverse canal section when the reciprocal member is in the second position.
    In order to provide tight sealing of the second transverse canal section, the following embodiment is useful, wherein the second transverse canal section at the bushing has a canal entrance opening with a diameter d, and the reciprocal member has a first diameter D which is larger than d. The reciprocal member is then pressed in a tightening manner against the canal entrance opening in the first transverse canal section by pressurized lubricant, or other pressurised liquid for the event that the valve system is used for other liquids than lubricant.
    For example, in the stationary valve member, a first canal and a second canal are provided parallel to the cylinder axis and on different sides of the bushing. The first canal is connected to the bushing through the first transverse canal section, and the second canal is connected to the bushing through the second transverse canal section.
    It is pointed out that the valve system has a general character such that it is not limited to lubricant injectors but can be used in other apparatus as well and, correspondingly, for other liquids. However, it is very advantageous for lubricant injectors, especially for the inlet valve.
    DK 2017 70940 A1
    In this case of the valve system is used as an inlet-valve system of the injector, the first position of the reciprocal member is an idle position for the idle phase and the second position of the reciprocal member is an injection position for the injection phase. The first canal and the second canals, which are provided on different sides of the bushing are optionally provided in the stationary valve member, as described above, but can alternatively be provided in the surrounding housing, for example in a flow chamber that connects the base of the injector with the nozzle if the stationary valve member is provided at least partly inside such flow chamber. The first canal communicates with the lubricant inlet port and the second canal communicates with the outlet valve system. Accordingly, for the idle phase, the throughput section of the reciprocal member is arranged for being remote from the transverse canal in the idle position for closing the transverse canal and preventing flow of lubricant from the first transverse canal section to the second transverse canal section. For the injection phase, the throughput section of the reciprocal member is arranged for being aligned with the transverse canal only in the injection position for flow of lubricant serially from the inlet port through the first canal, then through the first transverse canal section, then through the throughput section, then through the second transverse canal section and then through the second canal and to the outlet valve system in the injection phase.
    In further embodiments, the inlet-valve system further comprises an electricallydriven rigid displacement-member, for example push-member, for displacing, for example pushing, the reciprocal member from the idle position to the injection position.
    In a practical embodiment, the displacement-member is connected to an arrangement of a plunger and solenoid for upon electrical excitation of the solenoid to drive the displacement-member, for example push-member. Optionally, the displacementmember is connected to the plunger, whereas the solenoid is stationary in the injector. Alternatively, the displacement-member is connected to the solenoid, which is movable together with the displacement-member. After the injection phase, the motion of the displacement-member is reversed and the reciprocal member is caused to return to the idle position. In some practical embodiments, the displacement member is a rigid rod.
    DK 2017 70940 A1
    In principle, the displacement-member can be fastened to the reciprocal member, for pushing or pulling the reciprocal member between the idle position and the injection position. However, typically, for sake of constructional ease and other practical reasons, the displacement-member is not fastened to the reciprocal member.
    Especially, in order to increase the opening speed of the inlet-valve system, the following embodiment has been found useful. In this case, the displacement-member is a push-member, for example rigid push-rod, that is not fastened to the reciprocal member. Further, while in an idle position, the push-member is provided at a distance from the reciprocal member, for example between 0.1 and 2 mm, optionally between 0.2 and 1 mm. By the control signal from the controller, the push-member is accelerated towards the reciprocal member, obtains speed prior to impact with the reciprocal member, and displaces the reciprocal member from the idle position by the impact. Because the push-member is accelerated over a distance prior to impact with the reciprocal member, the displacement of the reciprocal member, from the idle position is abrupt, and the results is a very short opening time of the inlet valve with a consequently high degree of precision in timing.
    In some embodiments, the push-member is a push-rod, optionally connected to the plunger for displacement together with the plunger upon excitation of the solenoid. For example, the push-rod has a first end for impact with the reciprocal member for displacing the reciprocal member by impact with the first end.
    For example, in operation the injector is activated by sending an electrical control signal from the controller to the electrically-driven inlet-valve system when starting an injection phase. The control signal is causing displacement of reciprocal member from its idle position to its injection position and as a consequence thereof causing flow of lubricant from the lubricant feed conduit through the lubricant inlet port, through the inlet-valve system and into the conduit that flow-connects the inlet-valve system with the outlet-valve system. By the lubricant flow into the conduit pressure in the conduit and at the outlet-valve system is increasing and causing the outlet-valve system to open for flow of lubricant from the conduit to the nozzle aperture such that lubricant is injected into the cylinder through the nozzle aperture. At the end of the
    DK 2017 70940 A1 injection phase, the electrical control signal from the controller to the inlet valve system is changed, which is displacing the reciprocal member back into the idle position, causing the inlet-valve system to close for lubricant supply from the lubricant inlet port to the outlet-valve system.
    The separation of inlet-valve system and outlet-valve system reduced the total mass that has to be moved during operation. This accounts in particular for the small reciprocal member, as the small mass reduces reaction time of the movable objects, why the system implies an increased reaction speed and corresponding precision with respect to timing and amount. Optionally, the electrically controlled inlet-valve system with the displacement member, for example push-rod, implies a sudden impact on the reciprocal member, such that the onset of injection is very abrupt and, therefore, precise.
    For example, the injectors comprise a nozzle with a nozzle aperture of between 0.1 and 1 mm, for example between 0.2 and 0.5mm, and are configured for ejecting a spray of atomized droplets, which is also called a mist of oil.
    A spray of atomized droplets is important in SIP lubrication, where the sprays of lubricant are repeatedly injected by the injectors into the scavenging air inside the cylinder prior to the piston passing the injectors in its movement towards the TDC. In the scavenging air, the atomized droplets are diffused and distributed onto the cylinder wall, as they are transported in a direction towards the TDC due to a swirling motion of the scavenging air towards the TDC. The atomization of the spray is due to highly pressurized lubricant in the lubricant injector at the nozzle. The pressure is higher than 10 bars, typically between 25 bar and 100 bar for this high pressure injection. An example is an interval of between 30 and 80 bars, optionally between 35 and 60 bars. The injection time is short, typically in the order of 5-30 milliseconds (msec). However, the injection time can be adjusted to 1 msec or even less than 1 msec, for example down to 0.1 msec. Therefore imprecisions of only a few msec may alter the injection profile detrimentally, why high precision is required, as already mentioned above, for example a precision of 0.1 msec.
    DK 2017 70940 A1
    Also, the viscosity influences the atomization. Lubricants used in marine engines, typically, have a typical kinematic viscosity of about 220 cSt at 40°C and 20 cSt at 100°C, which translates into a dynamic viscosity of between 202 and 37 mPa s. An example of a useful lubricant is the high performance, marine diesel engine cylinder oil ExxonMobil® Mobilgard™ 560VS. Other lubricants useful for marine engines are other Mobilgard™ oils as well as Castrol® Cyltech oils. Commonly used lubricants for marine engines have largely identical viscosity profiles in the range of 40-100°C and are all useful for atomization, for example when having a nozzle aperture diameter of 0.1-0.8 mm, and the lubricant has a pressure of 30-80 bars at the aperture and a temperature in the region of 30-100°C or 40-100°C. See also, the published article on this subject by Rathesan Ravendran, Peter Jensen, Jesper de Claville Christiansen, Benny Endelt, Erik Appel Jensen, (2017) Rheological behaviour of lubrication oils used in two-stroke marine engines, Industrial Lubrication and Tribology, Vol. 69 Issue: 5, pp.750-753, https://doi.org/10.1108/ILT-03-2016-0075.
    SHORT DESCRIPTION OF THE DRAWINGS
    The invention will be explained in more detail with reference to the drawing, where FIG. 1 is a sketch of part of a cylinder in an engine;
    FIG. 2 is a drawing of an injector housing in a) an overview drawing and b) in an enlarged drawing;
    FIG. 3 is a drawing of a first embodiment of an outlet valve system, with a) a nonreturn ball valve and b) an alternative outlet valve system;
    FIG. 4 is a drawing of a second embodiment of an outlet valve system.
    DETAILED DESCRIPTION / PREFERRED EMBODIMENT
    FIG. 1 illustrates one half of a cylinder 1 of a large slow-running two-stroke engine, for example marine diesel engine. The cylinder 1 comprises a cylinder liner 2 on the inner side of the cylinder wall 3. Inside the cylinder wall 3, there are provided a plurality of injectors 4 for injection of lubricant into the cylinder 1. As illustrated, the injectors 4 are distributed along a circle with the same angular distance between adjaDK 2017 70940 A1 cent injectors 4, although this is not strictly necessary. Also, the arrangement along a circle is not necessary, seeing that an arrangement with axially shifted injectors is also possible, for example every second injector shifted relatively to a neighbouring injector.
    Each of the injectors 4 has a nozzle 5 with a nozzle aperture 5’ from which a fine atomized spray 8 with miniature droplets 7 is ejected under high pressure into the cylinder 1.
    For example, the nozzle aperture 5’ has a diameter of between 0.1 and 0.8 mm, such as between 0.2 and 0.5 mm, which at a pressure of 10-100 bars, for example 25 to 100 bars, optionally 30 to 80 bars or even 50 to 80 bars, atomizes the lubricant into a fine spray 8, which is in contrast to a compact jet of lubricant. The swirl 14 of the scavenging air in the cylinder 1 transports and presses the spray 8 against the cylinder liner 2 such that an even distribution of lubrication oil on the cylinder liner 2 is achieved. This lubrication system is known in the field as Swirl Injection Principle, SIP.
    However, also other principles are envisaged in connection with the improved lubrication system, for example injectors that have jets directed towards the cylinder liner.
    Optionally, the cylinder liner 2 is provided with free outs 6 for providing adequate space for the spray 8 or jet from the injector 4.
    The injectors 4 receive lubrication oil through a feed conduit 9, typically through a common feed conduit 9, from a lubricant supply 9’, for example oil circuit, of the engine. For example, the pressure in the supply conduit 12 is in the range of 25 to 100 bars, optionally 30 to 80 bars, which is a typical range of pressure for SIP valves.
    The injectors 4 are provided with electrical connectors 10’ that are electrically communicating with a controller 11 through electrical cables 10. The controller 11 sends electrical control signals to the injectors 4 for controlling injection of lubricant by the injector 4 through the nozzle 5. As it is illustrated, one cable 10 is provided for each injector 4, which allows individual control of injection by the respective injector 4.
    DK 2017 70940 A1
    However, it is also possible to provide one electrical cable 10 from the controller 11 to all injectors 4 such that all injectors 4 are injecting simultaneously upon receiving an electrical control signal through one single electrical cable 10. Alternatively, it is also possible to provide one electrical cable 10 from the controller 11 to a subgroup of injectors 4, for example a subgroup of 2, 3, 4, 5 or 6 injectors, such that a first subgroup is controlled by the controller 11 through a first cable 10 and a second subgroup is controlled through a second cable 10. The number of cables 10 and subgroups are selective dependent on preferred configurations.
    The electrical control signals from the controller 11 to the injectors 4 are provided in precisely timed pulses, synchronised with the piston motion in the cylinder 1 of the engine. For the synchronisation, the controller system 11 is electronically connected a computer 11 ’ that monitors parameters for the actual state and motion of the engine, for example speed, load, and position of the crankshaft, as the latter reveals the position of the pistons in the cylinders. The computer 1Γ and the controller system 11 are optionally combined. The controller 10 in cooperation with the computer 11’ determines the time length of the injection phase by the time that current is provided through the electrical cable or cables 10.
    FIG. 2a illustrates an injector housing 21 of an injector 4. The injector housing 21 is to be connected to a nozzle 5, for example of the type as in FIG. 3a, FIG. 3b or of the type as in FIG. 4. The housing 21 comprises a base 30 and a tubular flow chamber 16, which is a rigid hollow rod that rigidly connects the base 30 with the nozzle 5. The flow chamber 16 is sealed against the base 30 by an O-ring 22.
    The base 30 comprises a lubricant inlet port 12 for receiving lubricant from the lubricant feed conduit 9. The inlet port 12 is communicating with an inlet-valve system 13 for regulating the amount of lubricant received from the lubricant feed conduit 9 and delivered to the nozzle 5 through the hollow part 16’ of the flow chamber 16 during an injection phase.
    For regulating the lubricant that is dispensed through the nozzle aperture 5’ the injector 4 also comprising an outlet-valve system 15.
    DK 2017 70940 A1
    FIG. 3a shows an exemplified embodiment of an outlet valve system 15 that is part of the nozzle 5. The outlet-valve system 15 comprises an outlet non-retum outlet-valve
    17. In the outlet non-return outlet-valve 17, an outlet-valve member 18, exemplified as a ball, is pre-stressed against an outlet-valve seat 19 by an outlet-valve spring 20. Upon provision of pressurised lubricant in the hollow part 16’ of the flow chamber 16, the pre-stressed forced of the outlet-valve spring 20 is counteracted by the lubricant pressure, and when the pressure gets higher than the spring force, the outlet-valve member 18 is displaced from its outlet-valve seat 19, and the outlet non-return outletvalve 17 opens for injection of lubricant through the nozzle aperture 5’ into the cylinder 1. As exemplified, the outlet-valve spring 20 acts on the valve member 18 in a direction away from the nozzle aperture 5’. However, the configuration could be different with respect to the direction of the force of the outlet-valve spring 20 on the outlet-valve member 18 relatively to the nozzle aperture 5’, as long as the outlet nonreturn valve 17 is closing for the supply of lubricant to the nozzle aperture 5’ when in an idle state. The closing of the non-return outlet-valve 17 in an idle state prevents unintended flow of lubricant from the flow chamber 16 through the nozzle aperture 5’ into the cylinder 1 between injection phases.
    FIG. 3b illustrates a second, alternative embodiment of an outlet-valve system 15. The generalised principle of the outlet-valve system 15 is similar to the one disclosed in WO2014/048438. This reference also provides additional technical details as well as explanations to the functioning of the injector presented here, which are not repeated here, for convenience. A nozzle aperture 5’ is provided in the nozzle 5 tip for ejection of lubrication oil. Inside a cavity 40 of the nozzle 5, an outlet-valve member 18 is provided, the outlet-valve member 18 comprising a stem 41 and a cylindrical sealing head 42 which is arranged slidingly in a cylindrical cavity part 43 at the nozzle tip 44. The position of the valve member 18 is pre-stressed backwards away from the nozzle tip 44 by a spring 45 and is offset forwards by oil pressure acting through a channel 46 upon the back part 47 of the stem 41, the oil pressure acting against the spring force. The nozzle aperture 5’ is sealingly covered by the sealing head 42 which abuts the cylindrical cavity part 43 at the nozzle tip 44, unless the valve member 18 is pushed forward such that the sealing head 43 slides pass and away from the nozzle aperture 5’
    DK 2017 70940 A1 to allow lubricant oil to flow from the inner cavity 46 through the nozzle aperture 5’ for ejection.
    In FIG. 2b, the inlet valve system 13 is shown enlarged. It comprises a stationary valve member 23 that comprises a longitudinal bushing 24 in which a reciprocal member 25 is slidingly arranged. The reciprocal member 25 is tightly fitting inside the bushing 24 such that lubricant is not flowing between the outer side of the reciprocal member 25 and the inner side of the bushing 24. The reciprocal member 25 comprises a throughput section, exemplified as a narrowing section 25A, the function of which will be explained below. It is pointed out that the throughput section could also be a channel provided transversely in the reciprocal member 25.
    The stationary valve member 23 has a stationary rear part 23A and a stationary front part 23B, which in the exemplified embodiment are provided combined as a single piece. A first canal 26 is provided on one side of the valve member 23 and extending in a longitudinal direction of the flow chamber 16 along the valve member 23, and a second canal 27 is provided on the opposite side of the valve member 23 and extending in a longitudinal direction of the flow chamber 16 along the valve member 23. The longitudinal direction is identical to the cylinder axis of the reciprocal member 25 and the bushing 24. A transverse canal 28 is provided in the valve member 23 for connecting the first canal 26 with the second canal 27. However, a connection between the first canal 26 and the second canal 27 is only made when the reciprocal member 25 is moved forward towards the nozzle 5 so that the throughput section, exemplified as a narrowing section 25A, is flush with the transverse canal 28.
    The reciprocation of the reciprocal member 25 is provided by a displacement-member 31, exemplified as a push-rod, which is fastened to a reciprocal plunger 33 that is driven by a solenoid coil 32. The displacement-member 31 acts on a head 29 that is reversely spring loaded by helical spring 34. The head 29 is fastened to the reciprocal member 25 and moves together with it. The plunger 33, head 29, and the reciprocal member 25 are retracted by the spring 34 when in idle condition. When the solenoid coil 32 is excited by electrical current, the plunger 33 is moved forward towards the nozzle, which in turn moves the head 29 and the reciprocal member 25 forward
    DK 2017 70940 A1 against the force of the spring 34 until the head 29 comes to a halt against a stop 35, which in the current example is provided by the rear part 23A of the stationary valve member 23. At the most forward position of the reciprocal member 25, the narrowing section 25A of the reciprocal member 25 is flush with the transverse canal 26.
    When the lubricant inlet port 12 receives lubricant from the feed conduit 9, the lubricant flows through the inlet port 12 and through a rear passage 36 into a rear chamber 37 in which also the spring 34 is located. From the rear chamber 37, the oil flows into the first canal 26 and into the front part of the bushing 24. The lubricant also flows from the first canal 26 into the first transverse canal section 28A of the transverse canal 28, but not through the transverse canal 28 and to the second canal 27 due to the blocking of the transverse canal 28 by the reciprocal member 25.
    Due to the lubricant pressure, the reciprocal member 25 is pressed against the entrance opening 28C of the second transverse canal section 28B. As illustrated, a tight sealing is achieved, if the reciprocal member 25 is cylindrical with a diameter D that is larger than the diameter d of the second transverse canal section 28B of the transverse canal 28.
    When the solenoid coil 32 is excited by electrical current, the reciprocal member 25 is pushed forward, until the narrowing section 25A of the reciprocal member 25 is flush with the transverse canal 28, and lubricant can flow from the first canal 26 into the first transverse canal section 28A of the transverse canal 28, and from the first transverse canal section 28A through the narrowing section 25A into the second transverse canal section 28B and further into the second canal 27 at the opposite end of the transverse canal 28. The second canal 27 is communicating with the hollow part 16’ so that the lubricant can flow to the nozzle 5 from the second canal 27. As the lubricant is sufficiently pressurised, the lubricant will open the outlet valve 26 and be ejected from the nozzle aperture 5’ into the cylinder 1 of the engine.
    When the solenoid 32 is de-excited again at the end of the injection phase, the spring 34 presses the head 29 and the plunger 33 as well as the reciprocal member 25 again back from the forward injection position to the idle rearward position.
    DK 2017 70940 A1
    FIG. 4a illustrates an outlet valve system 15 in a closed state and FIG. 4b in an open state. The outlet valve system 15 is provided with an alternative non-retum outletvalve 17’, which is constructed similarly to the principle of the inlet valve system 13. Also, in this case, the outlet valve system 15 is provided in the nozzle 5. However, this is not strictly necessary, as it can also be provided upstream of the nozzle 5.
    Similarly to the inlet valve system 13, the alternative outlet valve system 15 comprises a stationary valve member 23 with a rear part 23A and a front part 23B, which in the exemplified embodiment are provided as a single piece. It comprises a longitudinal bushing 24 in which a reciprocal member 25 is slidingly arranged. The reciprocal member 25 is tightly fitting inside the bushing 24 such that lubricant is not flowing between the outer side of the reciprocal member 25 and the inner side of the bushing 24. The reciprocal member 25 comprises a narrowing section 25A, similarly to the function as explained in relation to FIG. 2b.
    A first longitudinal canal 26 is provided longitudinally on one side of the valve member 23 and a second canal 27 is provided longitudinally on the opposite side of the valve member 23. A transverse canal 28 is provided in the valve member 23 for connecting the first canal 26 and the second canal 27, however, a connection between the first canal 26 and the second canal 27 is only made when the reciprocal member 25 is moved forward towards the nozzle aperture 5’ such that the narrowing section 25A is flush with the first transverse canal section 28A and second transverse canal section 28B of transverse canal 28, which is illustrated in FIG. 4b. In this situation, lubricant can flow from the first canal 26 into the first transverse canal section 28A of the transverse canal 28, and from the first transverse canal section 28A around narrowing section 25A and into the second transverse canal section 28B and further into the second canal 27 on the opposite end of the transverse canal 28.
    The second canal 27 is communicating with a front chamber 40 that is provided around a further narrowing section 25B of the reciprocal member 25. A front part 25C of the reciprocal member 25 tightens the front chamber 40 against the pressure of the cylinder of the engine. It is pointed out that the front part 25C is arranged for sliding forward in open channel 39, which in turn communicates with the cylinder 1 of the
    DK 2017 70940 A1 engine. The front part 25C also tightly covers the nozzle aperture 5’. The tightening principle of the cylindrical front part 25C is similar to the prior art principle as disclosed in WO2014/04843 8.
    A forward motion of the reciprocal member 25 towards the nozzle aperture 5’ is effected by sufficiently pressurised lubricant from the hollow part 16’ acting on the head 29 against the power of the spring 34 and the against the pressure from the cylinder of the engine, which acts in the opposite direction on the end part 25C of the reciprocal member 25 in open channel 39. When the head 29 is pushed forward, lubricant flows around the head 29 into the first canal 26 and from the from the first canal 26 into the first transverse canal section 28A of the transverse canal 28, and from the first transverse canal section 28A through the narrowing section 25A into the second transverse canal section 28B and further into the second canal 27 on the opposite end of the transverse canal 28. From the second canal 27, the lubricant flows into front chamber 40. When the reciprocal member 25 is pushed sufficiently forward so that the end part 25C in the open channel 39 is pushed pass the nozzle aperture 5’, lubricant flows from front chamber 40 out of nozzle aperture 5’.
    As long as the pressure of the lubricant is high enough for holding the reciprocal member 23 in the forward position, lubricant will flow through the hollow part 16’and out of nozzle aperture 5’. Thus, the inlet valve system 13 and the outlet valve system 15 are open as long as the displacement-member 31 is keeping the inlet valve 12 open and pressurised lubricant is flowing through hollow part 16’ to the outlet valve system
    15.
    After the injection phase, the lubricant supply from the inlet port 12 to the nozzle 5 is stopped by cutting the current to the solenoid coil 32, which results in the head 29 and the displacement-member as well as the plunger 33 being pushed back by the spring 34 for an idle phase in the injection cycle.
    In principle, the valve in FIG. 4 can also be used as a hydraulic driven inlet valve.
    DK 2017 70940 A1
    Numbering cylinder cylinder liner cylinder wall lubricant injector nozzle
    5’ nozzle aperture free cut in liner atomised spray from a single injector 4 swirling spray lubricant feed conduit
    9’ lubricant supply electrical signal cable
    10’ electrical connection between electrical signal cable 10 and solenoid in injector 4 controller ’ computer lubricant inlet port of injector 4 inlet-valve system of injector 4 swirl in cylinder outlet-valve system of injector 4 flow chamber connecting housing 21 with outlet-valve system 15 and nozzle 5
    16’ hollow part of flow chamber 16 outlet non-retum valve, exemplified as outlet ball valve
    17’ outlet non-return valve, exemplified as stationary valve member 23 with reciprocal member 25 outlet-valve member, exemplified as ball outlet-valve seat outlet-valve spring injector housing
    O-ring at end of flow chamber 16 stationary valve member
    A rear part of the valve member 23
    23B front part of the valve member 23
    DK 2017 70940 A1 bushing around reciprocal member 25 electrically-driven cylindrical reciprocal valve member
    25A throughput section, exemplified as narrowing section of the reciprocal valve member
    25B further narrowing section of the reciprocal member 25 (in alternative outlet valve system)
    25C end part of the reciprocal member 25 first canal extending in a longitudinal direction of the flow chamber 16 second canal extending in a longitudinal direction of the flow chamber 16 transverse canal
    28A first transverse canal section of the transverse canal 28
    28B second transverse canal section of the transverse canal 28
    28C entrance of second transverse canal section 28B head of reciprocal member 25 (in alternative outlet valve system) base of injector housing 21 displacement-member, exemplified as push-member solenoid coil plunger in solenoid coil 32 spring 34 stop rear passage between inlet 12 and rear chamber 37 rear chamber of inlet valve system 13 end part of reciprocal member 25 (in alternative outlet valve system) open channel cavity stem cylindrical sealing head cylindrical cavity part nozzle tip spring channel back part of the stem 41
    DK 2017 70940 A1
    权利要求:
    Claims (24)
    [1] 1. A large slow-running two-stroke engine comprising a cylinder (1) with a reciprocal piston inside and with a plurality of injectors (4) distributed along a perimeter of the cylinder (1) for injection of lubricant into the cylinder (1) at various positions on the perimeter during injection phases; the engine further comprising a controller (11) for controlling the amount and timing of the lubricant injection by at least one of the injectors (4); wherein each injector (4) comprises
    - a nozzle (5) with a nozzle aperture (5’) extending into the cylinder (1) for injecting lubricant into the cylinder (1) in the injection phase;
    - an outlet-valve system (15) at the nozzle (5) for opening and closing for flow of lubricant to the nozzle aperture (5’) during an injection cycle; the outlet-valve system (15) being configured for opening for flow of lubricant to the nozzle aperture (5’) during an injection phase upon pressure rise above a predetermined limit at the outlet-valve system (15) and for closing the outlet-valve system (15) after the injection phase;
    - a lubricant inlet port (12) for receiving lubricant from a lubricant feed conduit (9); chracterized in that each injector (4) comprises an electrically-driven inlet-valve system (13) electrically connected to the controller (11) and arranged between the lubricant inlet port (12) and the nozzle (5) for regulating the lubricant that is dispensed through the nozzle aperture (5’) by opening or closing for lubricant flow from the lubricant inlet port (12) to the nozzle (5) in dependence of an electrical control-signal received from the controller (11); wherein the inlet-valve system (13) is arranged upstream of and remotely from the nozzle (5) and upstream of and remotely from the outlet-valve system (15).
    [2] 2. An engine according to claim 1, wherein the inlet-valve system (13) comprises a stationary valve member (23), the valve member (23) comprising a cylindrical bushing (24) inside which an electrically-driven cylindrical reciprocal member (25) is provided with a cylinder axis equal to a cylinder axis of the bushing (24); wherein the reciprocal member (25) is reciprocally movable inside the bushing (24) along
    DK 2017 70940 A1 the cylinder axis between an idle position for the idle phase and an injection position for the injection phase;
    wherein a first canal (26) is provided on one side of the bushing (24) and a second canal (27) is provided on another side of the bushing (24), wherein the first canal (26) communicates with the lubricant inlet port (12) and the second canal (27) communicates with the outlet valve system (15);
    wherein a transverse canal (28) extends through the stationary valve member (23) and through the bushing (24), for connecting the first canal (26) with the second canal (27) through the bushing (24); the transverse canal (28) having a first transverse canal section (28A) connecting the first canal (26) with the bushing (24) and a second transverse canal section (28B) connecting the bushing (24) with the second canal (27);
    wherein the reciprocal member (25) comprises a transverse throughput section (25A) for flow of lubricant through the reciprocal member (25) transversely to the cylinder axis; wherein the throughput section (25A) of the reciprocal member (25) is arranged for being remote from the transverse canal (28) in the idle position for closing the transverse canal (28) and preventing flow of lubricant from the first transverse canal section (28A) to the second transverse canal section (28B); and wherein the throughput section (25 A) of the reciprocal member (25) is arranged for being aligned with the transverse canal (28) only in the injection position for flow of lubricant serially from the inlet port (12) through the first canal (26) through the first transverse canal section (28A) through the throughput section (25A) through the second transverse canal section (28B) through the second canal (27) and to the outlet valve system (15) in the injection phase.
    [3] 3. An engine according to claim 2, wherein the throughput section (25A) is provided as a narrowing section for flow of lubricant from the first transverse canal section (28A) around the narrowing section (25A) in the bushing (24) and into the second transverse canal section (28B) in the injection phase.
    [4] 4. An engine according to claim 2 or 3, wherein the second transverse canal section (28B) at the bushing (24) has a canal entrance opening (28C) with a diameter d; wherein the reciprocal member (25) has a first diameter D which is larger than d
    DK 2017 70940 A1 for being pressed tightening against the canal entrance opening (28C) by pressure of lubricant in the first transverse canal section (28 A).
    [5] 5. An engine according to any one of the claims 2-4, wherein the reciprocal member (25) is pre-stressed into an idle position by a spring (34).
    [6] 6. An engine according to claim 5, wherein the inlet-valve system (13) further comprises an electrically-driven rigid displacement member (31) for displacing the reciprocal member (25) from the idle position to the injection position against the force of the spring (34).
    [7] 7. An engine according to claim 6, wherein the displacement member is a pushmember (31) for pushing the reciprocal member (25) from its idle position against the force of the spring (34) to its injection position, wherein the push-member (31) is not fastened to the reciprocal member (25); wherein the push-member (31) in the idle position is provided at a distance from the reciprocal member (25) and arranged for acceleration towards the reciprocal member (25) for obtaining speed prior to impact onto the reciprocal member (25) for displacing the reciprocal member (25) from the idle position to the injection position by the impact.
    [8] 8. An engine according to claim 6 or 7, wherein the electrically-driven rigid displacement -member (31) is connected to an arrangement of a plunger (33) and solenoid (32) for being driven upon electrical excitation and de-excitation of the solenoid (32).
    [9] 9. A method for lubricating a large slow-running two-stroke engine of the type comprising a cylinder (1) with a reciprocal piston inside and with a plurality of injectors (4) distributed along a perimeter of the cylinder (1) for injection of lubricant into the cylinder (1) at various positions on the perimeter during injection phases and further comprising a controller (11) for controlling the amount and timing of the lubricant injection by at least one of the injectors (4);
    wherein each injector (4) comprises
    DK 2017 70940 A1
    - a nozzle (5) with a nozzle aperture (5’) extending into the cylinder (1) for injecting lubricant into the cylinder (1) in the injection phase;
    - an outlet-valve system (15) at the nozzle (5) for opening and closing for flow of lubricant to the nozzle aperture (5’) during an injection cycle; the outlet-valve system (15) being configured for opening for flow of lubricant to the nozzle aperture (5’) during an injection phase upon pressure rise above a predetermined limit at the outlet-valve system (15) and for closing the outlet-valve system (15) after the injection phase;
    - a lubricant inlet port (12) for receiving lubricant from a lubricant feed conduit (9); chracterized in that each injector (4) comprises an electrically-driven inlet-valve system (13) electrically connected to the controller (11) and arranged between the lubricant inlet port (12) and the nozzle (5) for regulating the lubricant that is dispensed through the nozzle aperture (5’) by opening or closing for lubricant flow from the lubricant inlet port (12) to the nozzle (5) in dependence of an electrical control-signal received from the controller (11); wherein the inlet-valve system (13) is arranged upstream of and remotely from the nozzle (5) and upstream of and remotely from the outlet-valve system (15);
    the method comprising sending an electrical control signal from the controller (11) to the electrically-driven inlet-valve system (13) for starting an injection phase, and as a consequence thereof causing flow of lubricant from the lubricant feed conduit (9) through the lubricant inlet port (12), through the inlet-valve system (13), and into a conduit (16’) that flow-connects the inlet-valve system (13) with the outlet-valve system (15), by the lubricant flow into the conduit (16’) increasing pressure in the conduit (16’) and at the outlet-valve system (15), by the pressure rise causing the outlet-valve system (15) to open for flow of lubricant from the conduit (16’) to the nozzle aperture (5’) and injecting lubricant into the cylinder (1) through the nozzle aperture (5’); at the end of the injection phase, changing the electrical control signal from the controller (11) to the inlet valve system (13) and causing the inlet-valve system (13) to close for lubricant supply from the lubricant inlet port (12) to the conduit (16’).
    [10] 10. A method according to claim 9, wherein the inlet-valve system (13) comprises a stationary valve member (23), the valve member (23) comprising a cylindrical
    DK 2017 70940 A1 bushing (24) inside which an electrically-driven cylindrical reciprocal member (25) is provided with a cylinder axis equal to a cylinder axis of the bushing (24); wherein the reciprocal member (25) is reciprocally movable inside the bushing (24) along the cylinder axis between an idle position for the idle phase and an injection position for the injection phase;
    wherein a first canal (26) is provided on one side of the bushing (24) and a second canal (27) is provided on another side of the bushing (24), wherein the first canal (26) communicates with the lubricant inlet port (12) and the second canal (27) communicates with the outlet valve system (15);
    wherein a transverse canal (28) extends through the stationary valve member (23) and through the bushing (24), for connecting the first canal (26) with the second canal (27) through the bushing (24); the transverse canal (28) having a first transverse canal section (28A) connecting the first canal (26) with the bushing (24) and a second transverse canal section (28B) connecting the bushing (24) with the second canal (27);
    wherein the reciprocal member (25) comprises a transverse throughput section (25A) for flow of lubricant through the reciprocal member (25) transversely to the cylinder axis; wherein the throughput section (25A) of the reciprocal member (25) is arranged for being remote from the transverse canal (28) in the idle position for closing the transverse canal (28) and preventing flow of lubricant from the first transverse canal section (28A) to the second transverse canal section (28B); and wherein the throughput section (25 A) of the reciprocal member (25) is arranged for being aligned with the transverse canal (28) only in the injection position for flow of lubricant serially from the inlet port (12) through the first canal (26) through the first transverse canal section (28A) through the throughput section (25A) through the second transverse canal section (28B) through the second canal (27) and to the outlet valve system (15) in the injection phase;
    wherein the method comprises electrically driving the cylindrical reciprocal member (25) between the idle position and the injection position.
    [11] 11. An injector for an engine according to anyone of the claims 1-8 or for a method according to claim 9 or 10, wherein the injector (4) comprises
    DK 2017 70940 A1
    - a nozzle (5) with a nozzle aperture (5’) extending into the cylinder (1) for injecting lubricant into the cylinder (1) in the injection phase;
    - an outlet-valve system (15) at the nozzle (5) for opening and closing for flow of lubricant to the nozzle aperture (5’) during an injection cycle; the outlet-valve system (15) being configured for opening for flow of lubricant to the nozzle aperture (5’) during an injection phase upon pressure rise above a predetermined limit at the outlet-valve system (15) and for closing the outlet-valve system (15) after the injection phase;
    - a lubricant inlet port (12) for receiving lubricant from a lubricant feed conduit (9); chracterized in that each injector (4) comprises an electrically-driven inlet-valve system (13) arranged between the lubricant inlet port (12) and the nozzle (5) for regulating the lubricant that is dispensed through the nozzle aperture (5’) by opening or closing for lubricant flow from the lubricant inlet port (12) to the nozzle (5) in dependence of an electrical control-signal received from a controller (11); wherein the inlet-valve system (13) is arranged upstream of and remotely from the nozzle (5) and upstream of and remotely from the outlet-valve system (15).
    [12] 12. An injector according to claim 11, wherein the inlet-valve system (13) comprises a stationary valve member (23), the valve member (23) comprising a cylindrical bushing (24) inside which an electrically-driven cylindrical reciprocal member (25) is provided with a cylinder axis equal to a cylinder axis of the bushing (24); wherein the reciprocal member (25) is reciprocally movable inside the bushing (24) along the cylinder axis between an idle position for the idle phase and an injection position for the injection phase;
    wherein a first canal (26) is provided on one side of the bushing (24) and a second canal (27) is provided on another side of the bushing (24), wherein the first canal (26) communicates with the lubricant inlet port (12) and the second canal (27) communicates with the outlet valve system (15);
    wherein a transverse canal (28) extends through the stationary valve member (23) and through the bushing (24), for connecting the first canal (26) with the second canal (27) through the bushing (24); the transverse canal (28) having a first transverse canal section (28A) connecting the first canal (26) with the bushing (24) and
    DK 2017 70940 A1 a second transverse canal section (28B) connecting the bushing (24) with the second canal (27);
    wherein the reciprocal member (25) comprises a transverse throughput section (25A) for flow of lubricant through the reciprocal member (25) transversely to the cylinder axis; wherein the throughput section (25A) of the reciprocal member (25) is arranged for being remote from the transverse canal (28) in the idle position for closing the transverse canal (28) and preventing flow of lubricant from the first transverse canal section (28A) to the second transverse canal section (28B); and wherein the throughput section (25 A) of the reciprocal member (25) is arranged for being aligned with the transverse canal (28) only in the injection position for flow of lubricant serially from the inlet port (12) through the first canal (26) through the first transverse canal section (28A) through the throughput section (25A) through the second transverse canal section (28B) through the second canal (27) and to the outlet valve system (15) in the injection phase.
    [13] 13. An injector according to claim 12, wherein the throughput section (25A) is provided as a narrowing section for flow of lubricant from the first transverse canal section (28A) around the narrowing section (25A) in the bushing (24) and into the second transverse canal section (28B) in the injection phase.
    [14] 14. An injector according to claim 12 or 13, wherein the second transverse canal section (28B) at the bushing (24) has a canal entrance opening (28C) with a diameter d; wherein the reciprocal member (25) has a first diameter D which is larger than d for being pressed tightening against the canal entrance opening (28C) by pressure of lubricant in the first transverse canal section (28 A).
    [15] 15. An injector according to anyone of the claims 12-14, wherein the reciprocal member (25) is pre-stressed into an idle position by a spring (34).
    [16] 16. An injector according to claim 15, wherein the inlet-valve system (13) further comprises an electrically-driven rigid displacement member (31) for displacing the reciprocal member (25) from the idle position to the injection position against the force of the spring (34).
    DK 2017 70940 A1
    [17] 17. An injector according to claim 16, wherein the displacement member is a push-member (31) for pushing the reciprocal member (25) from its idle position against the force of the spring (34) to its injection position, wherein the pushmember (31) is not fastened to the reciprocal member (25); wherein the pushmember (31) in the idle position is provided at a distance from the reciprocal member (25) and arranged for acceleration towards the reciprocal member (25) for obtaining speed prior to impact onto the reciprocal member (25) for displacing the reciprocal member (25) from the idle position to the injection position by the impact.
    [18] 18. An injector according to claim 16 or 17, wherein the electrically-driven rigid displacement -member (31) is connected to an arrangement of a plunger (33) and solenoid (32) for being driven upon electrical excitation and de-excitation of the solenoid (32).
    [19] 19. An injector according to anyone of the claims 12-18, wherein the first canal (26) or the second canal (27) or both are provided in the stationary valve member (23).
    [20] 20. A valve system for a engine according to anyone of the claims 1-8 or for a method according to claim 9 or 10, or for an injector according to anyone of the claims 11-19, wherein the valve system (13, 15) comprises a stationary valve member (23), the valve member (23) comprising a cylindrical bushing (24) inside which a cylindrical reciprocal member (25) is provided with a cylinder axis equal to a cylinder axis of the bushing (24) and reciprocally movable inside the bushing (24) along the cylinder axis between a first position and a second position;
    wherein a transverse canal (28) extends through the stationary valve member (23) and through the bushing (24); the transverse canal (28) having a first transverse canal section (28A) on one side of the bushing and a second transverse canal section (28B) on another side of the bushing (24);
    wherein the reciprocal member (25) comprises a transverse throughput section (25A) for flow of the liquid through the reciprocal member (25) transversely to the cylinder axis; wherein the throughput section (25A) of the reciprocal member (25)
    DK 2017 70940 A1 is arranged for being remote from the transverse canal (28) in the first position for closing the transverse canal (28) and wherein the throughput section (25A) of the reciprocal member (25) is arranged for being aligned with the transverse canal (28) only in the second position for flow from the first transverse canal section (28A) through the throughput section (25A) to the second transverse canal section (28B).
    [21] 21. A valve system according to claim 20, wherein the throughput section (25A) is provided as a narrowing section for flow of lubricant from the first transverse canal section (28A) around the narrowing section (25A) in the bushing (24) and into the second transverse canal section (28B) when the reciprocal member (25) is in the second position.
    [22] 22. An valve system according to claim 20 or 21, wherein the second transverse canal section (28B) at the bushing (24) has a canal entrance opening (28C) with a diameter d; wherein the reciprocal member (25) has a first diameter D which is larger than d for being pressed tightening against the canal entrance opening (28C) by pressurized liquid in the first transverse canal section (28A).
    [23] 23. A valve system according to anyone of the claims 20-22, wherein the reciprocal member (25) is pre-stressed towards the first position by a spring (34).
    [24] 24. A valve system according to anyone of the claims 20-22, wherein a first canal (26) and a second canal (27) or provided in the stationary valve member (23) parallel to the cylinder axis and on different sides of the bushing, wherein the first canal (26) is connected to the bushing (24) through the first transverse canal section (28A), and the second canal (27) is connected to the bushing (24) through the second transverse canal section (28B).
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    KR20200096277A|2020-08-11|Large slow-acting two-stroke engine and method for lubrication thereof and controller for such engine and method
    DK179952B1|2019-10-25|A method for upgrading a lubrication system in a large slow-running two-stroke engine
    同族专利:
    公开号 | 公开日
    DK179954B1|2019-10-29|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    EP3904646A1|2018-10-02|2021-11-03|Hans Jensen Greentech APS|An improved lubricator pump unit and use of such lubricator pump unit|
    法律状态:
    2019-09-06| PAT| Application published|Effective date: 20190614 |
    2019-10-29| PME| Patent granted|Effective date: 20191029 |
    优先权:
    申请号 | 申请日 | 专利标题
    DKPA201770940A|DK179954B1|2017-12-13|2017-12-13|Large slow-running two-stroke engine and method of lubricating such engine, as well as an injector for such engine and method and a valve system|DKPA201770940A| DK179954B1|2017-12-13|2017-12-13|Large slow-running two-stroke engine and method of lubricating such engine, as well as an injector for such engine and method and a valve system|
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    JP2020532950A| JP2021507169A|2017-12-13|2018-12-13|Large low-speed two-stroke engines, methods of lubricating such engines, and injectors, valve systems, and their use for such engines and methods.|
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    JP2020147425A| JP2021011872A|2017-12-13|2020-09-02|Large slow-running two-stroke engine, method of lubricating such engine, and injector, valve system and use thereof for such engine and method|
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