EP3434872A1 - Dosierung von zylinderschmieröl bei grossen zylindern - Google Patents

Dosierung von zylinderschmieröl bei grossen zylindern Download PDF

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Publication number
EP3434872A1
EP3434872A1 EP18192829.2A EP18192829A EP3434872A1 EP 3434872 A1 EP3434872 A1 EP 3434872A1 EP 18192829 A EP18192829 A EP 18192829A EP 3434872 A1 EP3434872 A1 EP 3434872A1
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EP
European Patent Office
Prior art keywords
injector
cylinder
lubricating oil
valve
flow measuring
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Granted
Application number
EP18192829.2A
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English (en)
French (fr)
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EP3434872B1 (de
Inventor
Peer Bak
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Hans Jensen Lubricators AS
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Hans Jensen Lubricators AS
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/16—Controlling lubricant pressure or quantity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/14—Timed lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
    • F01M2001/083—Lubricating systems characterised by the provision therein of lubricant jetting means for lubricating cylinders

Definitions

  • the present invention concerns a dosing system for cylinder lubrication oil in large diesel engine cylinders, e.g. in marine engines, including:
  • the invention further concerns a method for dosing cylinder lubrication oil into large diesel engine cylinders, e.g. in marine engines, including the steps of:
  • the invention furthermore concerns an injector for use in a dosing system for cylinder lubrication oil in large diesel engine cylinders, e.g. in marine engines, including:
  • the invention is primarily intended for use in an electromagnetically controlled injector where the dosed amount is controlled via the opening time of a valve. This is different from other lubricating systems where the dosed amount is typically volumetrically controlled.
  • the dosed amounts of oil can e.g. be in atomised form with direct control of spray as the valve has a built-in pump. In a system operation will primarily be performed with a valve which can be controlled by an electromagnet.
  • EP 0 049 603 A1 is known an electromechanical injector.
  • a flow detector is used which has integrated switch function and which emits a signal when flow is present. The flow is monitored by the flow detector and the duration of the flow is compared with manually determined limit values. These are not flow measurements but only control of start and stop of a flow signal.
  • EP 1 426 571 is also known local injectors that are based on using a needle valve with a valve body in the form of a needle and a corresponding valve seat. If the needle is inclined relative to the seat or not aligned with the seat, a leak occurs. The needle is therefore to be guided so that the needle is not displaced radially relative to the valve seat. This is typically achieved by having fine tolerances and fit of needle and valve boring (needle guide) in which the needle is positioned. There are drawbacks by this design as the injectors typically have a considerable length since they extend through a relatively thick cylinder wall and lining.
  • the valve seat is to be as close as possible to the nozzle aperture in order to reduce the dead volume to be moved/accelerated before the valve begins to deliver the oil.
  • the object of the invention is to indicate an injector that contributes to avoid drawbacks of the prior art systems and which will be more robust/reliable and simple in operation.
  • the system according to the invention is peculiar in that the dosing system includes a flow measuring unit for each injector and/or for each cylinder, and that the flow measuring units are connected with the control unit for use in a closed circuit/loopregulation.
  • the method according to the invention is peculiar by a local flow measurement for each injector and/or a cylinder central flow measurement of the actually dosed amount of oil per injector, transmitting result of flow measurement to the control unit, comparing the flow measurement of the actually dosed amount of oil with an expected/planned amount of oil, and by the control unit transmitting a control signal to the opening/closing unit for regulating timing and amount of oil to the required extent.
  • the period from activating injector to start of flow signal can be used for adjusting the injection timing of the system. Allowance can thus be made for possible changes in timing (delayed and accelerated delivery of lubricating oil) due to viscosity conditions. Deviations in viscosity conditions are interesting since they determine timewise execution and can cause faster or slower timing for the injection.
  • the injector according to the invention is peculiar in that the opening/closing valve includes a ball valve body and an interacting valve seat, and that between the stem of the valve body and the wall in the valve guide of the opening/closing valve there is a gap with a width exceeding 10 ⁇ m.
  • the cross-sectional dimension of a nozzle aperture is typically the diameter of circular nozzle apertures.
  • the dosing system is peculiar in that the control unit includes a local control box for each cylinder, controlling timing and dosing of all injectors per cylinder.
  • the dosing system is peculiar in that four to ten injectors are used for each cylinder.
  • the dosing system is peculiar in that a local pressure accumulator is provided for each injector or for all the injectors associated with each individual cylinder.
  • each injector has an outlet for connection with a return line for conducting excess oil back to the lubricating oil supply or for performing pressure measurements.
  • the dosing system is peculiar in that each injector is made as a unit, that the opening/closing valve includes a ball valve body and an interacting valve seat, and that between the stem of the valve body and the wall in the valve guide of the opening/closing valve there is a gap with a width exceeding 10 ⁇ m.
  • the dosing system is peculiar in that each injector is made as a unit, that the opening/closing valve is an electromechanical valve integrated in the injector for dosing the lubricating oil, where the electromechanical opening/closing valve includes a spring-biased valve stem.
  • the dosing system is peculiar in that it includes flow measuring units with the same operation range for each injector and for each cylinder, and that the control unit is connected with all the flow measuring units and adapted for receiving signal from the flow measuring units at the injectors at relatively large flow rates and for receiving signal from the cylinder central flow measuring units at relatively small flow rates.
  • the dosing system is peculiar in that it includes flow measuring units with different operation range for each injector and for each cylinder, that the control unit is connected with all the flow measuring units, that the flow measurement units with the lowest operating range are the local flow measuring units which are connected with the injectors, and that the flow measuring units with the highest operating ranges are the cylinder central flow measuring units.
  • the dosing system is peculiar in that it only includes one cylinder central flow measuring unit which is combined with at least one local flow measuring unit connected with an injector.
  • the dosing system is peculiar in that it includes a combination of a cylinder local flow measuring unit and an injector local flowswitch.
  • the method is peculiar in that the injector local flow measurement is performed in combination with a central flow measurement per cylinder.
  • the injector local flow measurement is performed in combination with a central flow measurement per cylinder.
  • the cylinder central flowmeters are used. The reason for this is that it is necessary that the dosing amount per injector is to "cover" a relatively large area.
  • An alternative embodiment will be that instead of using the same flowmeters (with same capacity), one may use different flow measuring units with different flow ranges, where the flow measurement unit with the least flow range is situated locally on the individual injector and the flowmeter with the greatest flow range is situated centrally of the cylinder. This method provides that the flow measuring system can more easily provide more precise flow measurements over the whole flow range.
  • An alternative embodiment will be to combine a central flowmeter with minimum one flowmeter mounted on one of the injectors. In that way is provided a measuring system which can handle large as well as small flows and a cheaper and more maintenance-free setup where the number of flowmeters is limited.
  • the method is peculiar in that the supply pressure in the supply line is monitored.
  • the method is peculiar in that the supply pressure in the supply line is used as parameter for controlling the dosing amount.
  • the method is peculiar in that dosing of lubricating oil is performed by activating an opening/closing valve in the form of an electromechanical valve integrated in the injector for dosing the lubricating oil, for moving the valve stem of the opening/closing valve by injection of the lubricating oil.
  • the method is peculiar in that timing and dosing amount are controlled by the opening and closing time of the electromechanical valve.
  • the method is peculiar in that flow measuring units with the same operating range are established for each injector and for each cylinder, that the control unit is connected with all the flow measuring units, that by large flow rates measurements from local flow measuring units at the injectors are selected, and by relatively small flow rates the measurements from the cylinder central flow measuring units are selected.
  • the method is peculiar in that flow measuring units with different operation ranges are established for each injector and for each cylinder, that the flow measuring units with the lowest operating ranges are selected as the local flow measuring units which are connected with the injectors, and that the flow measuring units with the highest operating ranges are selected as the cylinder central flow measuring units.
  • the method is peculiar in that only one cylinder central flow measurement is performed, and that this is combined with at least one local flow measurement at an injector.
  • the method is peculiar in that flow measurement is performed as a combination of a cylinder local flow measurement with a cylinder local flow measuring unit and an injector local flow registration with an injector local flowswitch.
  • the injector is peculiar in that the valve seat is conical.
  • the injector is peculiar in that the area of the gap at least corresponds to the total area of the nozzle aperture(s) of the injector.
  • the injector is peculiar in that the injector includes a filter and that the gap of the opening/closing valve at least has the same width corresponding to half of the mesh width of the filter.
  • the injector is peculiar in that it includes an electromechanical actuator, preferably in the form of a solenoid valve or a piezo-electric element.
  • the injector is peculiar in that it has an outlet for connection with a return line for draining off excess oil or for performing pressure measurements.
  • the injector is peculiar in that the injector includes a flow sight glass or a flowswitch for visually or electronically indicating an actual flow.
  • the injector is peculiar in that it is adapted to operate at a supply pressure between 30 and 100 bar. According to a further embodiment of the invention, the injector is peculiar in that it is adapted to operate with compact jet(s).
  • the injector is peculiar in that it is adapted to operate with atomised spray(s).
  • the injector is peculiar in that the gap width between the stem of the valve body and a boring in which the stem is received is at least half the size of the cross-sectional dimension of a nozzle aperture.
  • a pulsating flow is to be measured concurrently.
  • the other injectors can automatically supplement/replace one or more failing injectors based on the control in the control unit and the closed circuit/loop regulation.
  • the opening/closing function of the dosing unit integrated in the injector while at the same time the control is designed so that based on actual measurement of consumption/flow, the delivered amounts can be controlled, hereby removing uncertainty due to viscosity (temperature, oil type), distances and diameters of supply lines.
  • an injector with integrated opening/closing valve preferably a solenoid valve
  • both piping and drawing of cables are appreciably simplified by only having one common supply line of pressurised lubricating oil (without need for a return line) provides that the dosing becomes proportional with the time where the opening/closing solenoid valve is open.
  • there is a separate local control box which is used for opening/closing the injector based on signals from the engine/control unit of the ship.
  • An electromechanically regulated injector designed for cylinder lubrication of large diesel engines entail advantages in relation to prior art lubricating systems. Systemwise it can regulate individually with regard to lubricating oil amount and timing.
  • the function is only dependent on a control box which can control each single injector separately or together with regard to timing and opening time. This can occur independently of other opening/closing valves and is only limited by the speed at which the opening/closing valve in an injector can execute the opening/closing cycle.
  • the measured flow is used for controlling the delivered amount in relation to the planned amount.
  • an associated local control box can correct the opening time for magnet valve(s) for the associated injector or injectors.
  • the injector is insensitive to particles which are smaller than the nozzle aperture and which are larger than the gap width. Operation can thereby be performed with a relatively coarse filtration of the oil. There is no risk of a valve body/ball will get stuck even if the oil contains small particles with sizes of 10 ⁇ m or larger. It will be no problem to operate with gap widths of 10 ⁇ m and up to 0.3 mm or larger in the opening/closing valve.
  • the seat in the valve is designed as the seat in a check valve, typically with a conical shape, and the oil pressure in the valve will together with a closing element/spring keep the valve closed.
  • valve seat which is self-adjusting, providing great reliability of the valve function in the injector.
  • An alternative embodiment could be that instead of using a flow measuring unit with direct measurement of flow, an indirect method for determining flow is used.
  • a flow measuring unit where a flowswitch (flow indicator) is used where it is presupposed that pressure and temperature are uniform such that the signal duration can be measured, thereby providing a signal which is proportional to the dosed amount to the control unit.
  • a flowswitch flow indicator
  • such an alternative embodiment can be provided in the form of a flow measurement unit where a ball is lifted off a ball seat and where a sensor is mounted for detecting this condition.
  • An alternative embodiment will be to design the dosing system such that a central flow measurement unit per cylinder is used, combining this with a number of injector local flowswitches (flow indicators) such that a total measurement of consumption is obtained while simultaneously providing certainty that a flow exist in all injectors.
  • the flow measurement of the dosing system is simplified as only monitoring of the total flow into the cylinder is performed, and where the local flow measurement units are replaced by simple flowswitches (typically one per injector) which only indicate the presence or absence of flow.
  • the flow measuring unit is connected to the control unit or local control boxes controlling the injectors for each individual cylinder, and herein the planned and actual flows are compared. In case of deviations, the flowswitches can be used for considering if some injectors have stopped operating.
  • An alternative embodiment to the above mentioned dosing system could be that the control unit or the local cylinder control boxes, in addition to measuring the total actual consumption per cylinder, simultaneously compare flowswitch signals between the various injectors associated with the same cylinder such that a warning or an alarm is triggered to the user if deviation exceeding a given value occur, for example 20% of the time there is a flow signal.
  • An alternative use of the above mentioned flow signal could be that the period of time from activation of the injector to flow pulse start on the flowmeter is measured. This measured value is compared with a system-specific check measurement of the time which passes between activation of injector to the injector starting to dose. Presumably, both of the measurements will lie so close to each other that the signal from the flow measurement unit always can be used directly without any problems. In this way it is possible to control if the timing, i.e. the time for activating the solenoid, has to be adjusted in case that the deviation attains a given value.
  • a further possible embodiment of a dosing system could include a flow measuring unit in the form of a traditional oval-rotor based flow measuring unit.
  • the drawback of this type of measuring unit is that typically it is not suited for a particularly large flow range as a given amount is required for turning the rotors one revolution, thereby causing emission of a signal.
  • the pulsating delivery of lubricating oil does not provide an even operation of the flow measurement unit.
  • it may be required to vary the period over which the pulses are counted.
  • the local control box is to vary the period of time in which flow pulses are counted, and at the same time preferably making a continuous calculation with continuously overlapping periods. Based on empirical experiments, for a given flow measurement unit the correlation between a given flow interval and the number of pulses is to be established which is to be integrated in the local control box.
  • a cylinder For a cylinder is used between four and ten injectors, depending on engine size and type.
  • the dosing system operates via a pressurised supply line with lubricating oil.
  • the lubricating oil is kept at a constant pressure, and with regard to minimising disturbances/variations in the pressurised supply line to the individual cylinders/injectors, there may be a need for disposing accumulators per injector and/or centrally per cylinder.
  • Timing of dosing the lubricating oil is either controlled locally or centrally.
  • the activation time is continuously adapted, depending on the reference signals of the engine.
  • control is to be capable of identifying any problems with one or more injectors.
  • the supply pressure can be monitored in the pressurised supply line.
  • a flow measurement unit can be used locally as well as having an additional control in the form of a central flow measurement unit.
  • system may compensate for variations in pressure and thereby in delivery amount as the individual opening/closing times can be adjusted individually.
  • injectors for a cylinder together ensure handling of errors, e.g. in the form of increasing the dosing amount at individual lubricating points or possibly via a cylinder central control box.
  • a control box controls timing and dosing of one or more injectors per cylinder, depending on reference signals from the engine (load, flywheel position and so on).
  • the local control box can be provided in immediate connection to an injector or alternatively be integrated in the individual injector.
  • the dosing amount is calculated from feed rate, choice of regulating algorithm, oil analyses, and other engine specific parameters, sulphur percentage, fuel type (residual TBN, Fe-contents etc.). These parameters are either read in automatically and directly or indirectly via a central control unit.
  • analysis of scavenge drain oil can be used as an active control parameter. Analysis of the drain oil can either be performed online or manually and on this background the amount of lubricating oil is regulated proportionally with the content of Fe particles. And if this does not improve the measured values within a given time, an alarm is raised.
  • the injector according to this invention is equipped with ball valve body and an interacting valve seat which is typically conical but which also can be formed with a shape corresponding to the shape of the ball. Sealing is ensured even by large gap areas such that the gap area is not flow limiting, meaning that the area of the gap is at least to correspond to the total nozzle aperture area such that in case of several nozzle apertures per injector, the sum of the nozzle aperture areas is used.
  • this can mean that the gap can be as small as 0.005 mm as a particle of about 0.01 mm can press the valve body to one side and increase the gap width to 0.01 mm.
  • passage of particles with a size of 0.01 mm can be allowed without blocking the movement of the valve body and without the valve leaking as the ball body will fit tightly to the seat.
  • the gap width (radius difference) will, however, typically be about 0.15 mm or more since the nozzle apertures of the injector are typically 0.3 mm or more.
  • filters can be coarser and allow for larger particles, depending on the size of the nozzle apertures.
  • the ball valve type can prevent dirt and particles from blocking the movement of the valve body as it can be operated in a secure way even with a large gap where there is spacing between the stem of the valve body and the boring such that the boring does not appear as a valve guide for the valve stem. Such a wide gap will make a needle valve unsuitable for the application.
  • the injector is simple to make, without close tolerances and complicated mounting.
  • the dosing system is simple to mount as there is only need for a common supply line per cylinder. All injectors are coupled on this supply line. There is no need for return lines, only an electric connection for each injector to a common control box which can be mounted locally on the individual cylinder. This provides serviceability and high reliability.
  • the solenoid in a solenoid valve can be a standard solenoid as used today.
  • the injector has low power consumption as only the required lubricating oil amount is to be pumped up to the pressure level for injection.
  • injector it is possible to make the injector more intelligent by expanding the system which is particular embodiments may include sensors that are able to measure pressure, temperature or to take oil samples for analysis. Pressure provides information about piston position determination and knowledge about the load on the engine. Temperature says something about the condition in the cylinder. Oil samples can form basis for evaluation of the lubrication condition. On the background of data, injection time and duration can be calculated from a given control algorithm in the control unit.
  • Each injector has its own time-controlled dosing unit where timing and dosing amount are controlled by the opening and closing times of the injector.
  • the injector can either be provided with an atomiser valve or a valve with one or more jets/compact jets.
  • the injector can be made in an embodiment where it only supplied with pressurised lubricating oil and without return lines. Typical supply pressures are between 30 and 100 bars.
  • the valve function of the injector is a ball valve.
  • the injector can be actuated electromechanically, for example in the form of a solenoid valve or piezo-mechanical element.
  • an alternative embodiment could be that the injector is equipped with a flow sight glass or a flowswitch for visually or electronically indicating an actual flow. In this way is provided a direct indication of the individual injector being active and functioning.
  • individual injectors are situated at difficult accessible locations, and here it will be advantageous with electronic monitoring which is detected locally but reported centrally.
  • An example of such a solution could be a conical boring in a ball control glass in which a sensor detecting a ball is disposed.
  • FIG. 1 shows a complete lubricating system for N cylinders 1.
  • Each cylinder is equipped with a number of X injectors 2 which are connected to a common lubricating oil supply line 31 having a constant supply pressure, e.g. in the magnitude 30 - 100 bars.
  • the supply pressure is delivered by a hydraulic pump unit 10 which is supplied from the day tank 1000.
  • the pump station 10 includes two pumps 11, two filters 12 and two check valves 13 preventing the lubricating oil from running back through a still-standing pump 11.
  • the pump station also includes two shut-off valves 14 that are inserted in the supply line 34 so that the filters 12 can be cleaned during operation.
  • the two pumps 11 are standby for each other and start up automatically in case of a drop in oil pressure.
  • a pressure valve 20 or a stepless electronically controllable pressure valve 115 (the figure shows the latter in principle).
  • the pressure in the supply line will be constant, and here is used a common pressure valve 20 where the pressure is constant.
  • the pressure valve 20 can be an electronically controlled pressure valve with adjustable pressure which via the connection 505 to the general control 200 or possibly to a cylinder local control box 100. This adjustable pressure can be used as a parameter for the dosed lubricating oil amount.
  • Each cylinder is provided a branch pipe 22 coupled to the main supply 31.
  • a flow measuring unit 4 that measures the actually supplied amount of lubricating oil.
  • the signal from the flow measuring unit 4 is transmitted to a local control box 100 where the measured value is compared with the expected flow, and depending on the size of the deviation, the control box 100 can adjust the opening time for the individual injectors 2 for the cylinder in question.
  • each injector 2 On each injector 2 is mounted an electromechanical valve with a solenoid 1014. By activating the solenoid 1014, the injector is opened and the lubricating oil is delivered.
  • the delivered amount of lubricating oil is proportional to the period in which the valve is kept open. However, this presupposes that the pressure in the supply line is constant, and for this purpose an accumulator 6 is provided.
  • a local control box 100 controlling opening/closing times for all associated injectors 2 are provided for each cylinder.
  • the injector 2 By activating the injector 2, the lubricating oil is conducted from the supply line 31 branch pipes 22 through the flow measuring unit 4 and via a branch line 21 respective injectors 2.
  • the flow measuring unit 4 that directly or indirectly measures the passing flow is connected to the local control box 100 where comparison between the expected and the actual flow is performed, from which possible corrections are calculated and the opening time for the solenoid 1014 of the injector is adjusted.
  • the accumulator 6 is provided between the flow measuring unit 4 and the branch piece 21 in order thereby to ensure an even flow across the flow measuring unit 4 where surges and return flow in the lubricating oil otherwise would disturb the flow measurement.
  • All the previously mentioned cylinder-specific control boxes 100 are connected to a main control box 200. From this main control box 200 operation information (e.g. planned lubricating oil amount) is transmitted to all connected units via signal cables 550 or via a network. In the same way, each local control box 100 also receives information about flywheel position via signal cables 601, and based on operational data from the main control box 200 the correct opening time and the associated opening period are controlled. In case of error, the local control box 100 triggers an alarm which is transmitted via signal cable 650 and via network.
  • operation information e.g. planned lubricating oil amount
  • each local control box 100 also receives information about flywheel position via signal cables 601, and based on operational data from the main control box 200 the correct opening time and the associated opening period are controlled. In case of error, the local control box 100 triggers an alarm which is transmitted via signal cable 650 and via network.
  • the main control box 200 receives and transmits information from the marine engine about actual load, feed rate, oil pressure and temperature, and revolutions, and on this basis the correct activation time is calculated.
  • this embodiment would require that all flywheel reference signals (via signal line 601) and load/index signals (via signal line 501) are delivered directly to the main control box 200 from where possible alarm signals are emitted (via signal line 506).
  • the solenoid valves 1013 of the individual injectors will be activated directly from the main control box 200 via signal lines 120 and control the opening and closing of solenoid valves: common, individual, or both.
  • Alarm signals are generated directly by the main control box and are transmitted via signal line 650 to the alarm system of the ship.
  • FIGS. 2.1 and 2.2 show an embodiment variant where the cylinder local control boxes 100 are instead integrated in the individual injectors 2, meaning that the cylinder local control boxes 100 are substituted by injector local control boxes 101.
  • injector local individual flow measuring units 4.X i.e. one flow measuring unit per injector 2
  • possible individual accumulators that also are disposed between the flow measuring units 4.X and the injectors (this embodiment is not shown on the drawings 2.1 and 2.2 where only one local accumulator 6 per cylinder is shown).
  • the embodiments shown here are identical with the system described on Figure 1 , i.e. the main control box 200 is also used here.
  • the main control box 200 is now only processing the signals from the individual injectors and no longer the cylinderwise signals.
  • Figure 3 shows an alternative embodiment where all injectors are activated simultaneously such that the solenoids 1014 (associated with the cylinder concerned) are activated at once via a cable 120 that serially connects all the solenoids 1014 on the injectors associated with the same cylinder.
  • this embodiment there is a cylinder local control box 100 controlling all injectors and where cylinder local flow measuring units and possible accumulators are applied. This means that the system becomes more integrated and simple.
  • a possible alternative embodiment could be that instead of the cylinder local control box 100 mentioned in Figure 3 , one injector local control box could control the remaining injectors based on one cylinder local flow measurements. As mentioned in connection with Figures 2.1 and 2.2 , this variant will mean that one cylinder local control box is replaced by one injector local control box. Such an embodiment will be the absolutely most simple with a minimum of cables, flowmeters etc.
  • injector local control boxes each controlling all injectors for one cylinder and independently of all others. If this is combined with a monitoring function in the active injector local control box 101, a redundant system can be built up where the succeeding injector is instructed to take over, e.g. via a relay access and a cable, due to error in a preceding injector. Finally, the injector local control box could be made to trigger an alarm when it fails when the preceding injector is failing at the same time.
  • FIG. 4 shows an injector as can be used in a system of the above mentioned type. On the Figure is shown that each cylinder 1 has a number of injectors 2 (four are shown per cylinder on the drawing). Pressurised oil is supplied through the branch pipe 21 to the injector 2 through supply channel 20100.
  • the injector shown in Figures 4 and 5 includes a nozzle 1001 which via an external screw thread is mounted in an internal valve housing 1006.
  • the valve housing 1006 itself has a flange that partially rests upon the injector housing 1017 itself and partially upon an assembly flange 1007.
  • the injector housing 1017 is fitted externally of the assembly of nozzle 1001 and valve housing 1006, and where the injector housing 1017 is mounted in a flange, e.g. by an interference fit.
  • the internal valve housing 1006 consists of a flange with an O-ring groove and a subsequent turning that makes the valve housing 1006 continue a length up into the solenoid core/armature housing 1009.
  • the O-ring 1008 ensures that the pressurised oil remains within valve housing 1006 and solenoid core/armature housing 1009.
  • solenoid core/armature housing 1009 Around solenoid core/armature housing 1009 is provided a main flange 1010 which via screws 1011 clamps injector housing with nozzle, solenoid core/armature housing 1009 and assembly flange 1007.
  • the nozzle/valve housing assembly 1001/1006 is located in the injector housing and by means of an O-ring 1002 it is ensured that no dirt or oil residues enter farther up in the injector housing 1017.
  • valve body/armature housing 1009 In the solenoid core/armature housing 1009 is located an armature/piston 1012 with an internal screw thread where the valve body 1003 is mounted, and where the threaded joint is secured by a pointed screw 1013. In the armature 1012 there are some channels 1023 for conducting the pressurised oil on in direction towards the nozzle. The possible travel of valve body/armature 1003/1012 is given by the cavity 20200.
  • the oil is conducted through the injector via the cavity 20200 and through the channel 1023.
  • the oil then continues out into the cavity 1022 and through the channel 1021 to the cavity 1020 from where the oil is conducted on via the gap 1030 to the cavity around the ball valve seat 1019.
  • the gap is formed between the valve body stem 1003 and the wall 1031 in the boring in which the valve body stem is received.
  • valve body 1003 When the solenoid 1014 is activated, the valve body 1003 is moved in direction against the solenoid 1014 until the cavity 20200 is filled by the armature/piston 1012. When the valve body 1003 with integrated ball 1016 is lifted off the ball seat 1019, pressurised oil is conducted through the valve seat 1019 via the channel 1018 out through the nozzle aperture 1040. When the electric signal through line 120 from the control box 100 to the injector solenoid 1013 is switched off, the spring 1005 ensures that the injector 2/ball seat 1019 is closed by pressing the valve body 1003 and armature/piston 1012 in direction against the ball seat 1019.
  • the spring 1005 shown in Figure 4 ensures that the valve is closed when the solenoid 1013 is switched off.
  • the spring force can be adjusted by adjusting the compression of the spring by a setting the position of the nut 1004.
  • the necessary spring force for providing a satisfactorily rapid closing of the valve can be determined by empirical experiments as a compromise between solenoid fore and spring force is to be found; hence the compression will be constant and the "nut" be integrated in the valve body in the form of a rest/collar on which the spring bears.
  • the injector valve function is performed by a ball valve body such as shown on Figure 4 . It is possible to use injectors that spray and/or form oil jets, and to use injectors with one or more nozzle apertures 1040.
  • the injector controls by an electric signal 120 that enables free and independent control of when the injector/valve is to open and close, and thereby the opening period.
  • Figure 5 shows in principle a system that functionally corresponds to the system of Figure 4 , however provided with an alternative embodiment for an injector where it is possible to provide pressure measurements or samples of possible lubricating oil residue from the cylinder through an outlet 20000 at the side of the flange. Externally of the nozzle/valve housing 1001/1006, the injector has a gap relative to the injector housing 1017, and through this gap there is communication to the outlet 20000.
  • the invention comprises at least some of the following aspects:

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Catching Or Destruction (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
EP18192829.2A 2011-03-18 2012-03-16 Dosierung von zylinderschmieröl bei grossen zylindern Expired - Fee Related EP3434872B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DKPA201170129A DK177258B1 (da) 2011-03-18 2011-03-18 Doseringssystem for cylindersmøreolie til store cylindre samt fremgangsmåde til dosering af cylindersmøreolie til store cylindre
PCT/DK2012/050079 WO2012126473A2 (en) 2011-03-18 2012-03-16 Dosing of cylinder lubricating oil into large cylinders
EP12716211.3A EP2686527B1 (de) 2011-03-18 2012-03-16 Einspeisung von schmierstoff in zylinder

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP12716211.3A Division EP2686527B1 (de) 2011-03-18 2012-03-16 Einspeisung von schmierstoff in zylinder
EP12716211.3A Division-Into EP2686527B1 (de) 2011-03-18 2012-03-16 Einspeisung von schmierstoff in zylinder

Publications (2)

Publication Number Publication Date
EP3434872A1 true EP3434872A1 (de) 2019-01-30
EP3434872B1 EP3434872B1 (de) 2021-11-10

Family

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Family Applications (3)

Application Number Title Priority Date Filing Date
EP12716211.3A Active EP2686527B1 (de) 2011-03-18 2012-03-16 Einspeisung von schmierstoff in zylinder
EP18192829.2A Expired - Fee Related EP3434872B1 (de) 2011-03-18 2012-03-16 Dosierung von zylinderschmieröl bei grossen zylindern
EP13188526.1A Active EP2722500B1 (de) 2011-03-18 2012-03-16 System und Verfahren zur Dosierung von Schmieröl in große Dieselmotorzylinder

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP12716211.3A Active EP2686527B1 (de) 2011-03-18 2012-03-16 Einspeisung von schmierstoff in zylinder

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP13188526.1A Active EP2722500B1 (de) 2011-03-18 2012-03-16 System und Verfahren zur Dosierung von Schmieröl in große Dieselmotorzylinder

Country Status (9)

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EP (3) EP2686527B1 (de)
JP (4) JP2014508890A (de)
KR (3) KR102002181B1 (de)
CN (2) CN103939174B (de)
DK (4) DK177258B1 (de)
HK (1) HK1197094A1 (de)
RU (2) RU2586420C2 (de)
SG (2) SG10201809580TA (de)
WO (1) WO2012126473A2 (de)

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DK178164B1 (en) * 2014-07-29 2015-07-13 Hans Jensen Lubricators As A method for lubricating large slow running two-stroke diesel engines
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DK179113B1 (en) 2015-04-29 2017-11-06 Hans Jensen Lubricators As Lubricant injector for large slow-running two-stroke engine and production method
DK178427B1 (en) * 2015-04-29 2016-02-22 Hans Jensen Lubricators As Lubricant injector for large slow-running two-stroke engine and production method
DK3368751T3 (en) * 2015-10-28 2022-05-02 Hans Jensen Lubricators As A large slow-running two-stroke engine with sip lubricant injector
DK178732B1 (da) * 2016-03-23 2016-12-12 Hans Jensen Lubricators As Fremgangsmåde og anlæg til dosering af smøreolie i cylindre, fortrinsvis i 2-takts dieselmotorer samt anvendelse af sådan fremgangsmåde og anlæg
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CN106567960B (zh) * 2016-10-17 2019-07-05 潍柴动力股份有限公司 一种电磁阀的控制方法和系统
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US10126152B1 (en) 2017-07-25 2018-11-13 Ecolab Usa Inc. Fluid flow meter with linearization
US10935407B2 (en) 2017-07-25 2021-03-02 Ecolab Usa Inc. Fluid flow meter with viscosity correction
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DK179750B1 (en) 2017-12-13 2019-05-07 Hans Jensen Lubricators A/S Large slow-running two-stroke engine and method of lubri-cating such engine, as well as an injector with an electric pumping system for such engine and method
EP3724463B1 (de) * 2017-12-13 2024-01-31 Hans Jensen Lubricators A/S Ein injektor für einen grossen, langsam laufenden zweitaktmotor und verfahren zum schmieren eines solchen motors, sowie ein solcher motor
DK179945B1 (en) * 2017-12-13 2019-10-21 Hans Jensen Lubricators A/S A large slow-running two-stroke engine and a method of lubricating it and a controller for such engine and method
DK179946B1 (en) 2018-07-06 2019-10-21 Hans Jensen Lubricators A/S A METHOD FOR OPTIMIZING LUBRICATION IN A LARGESLOW RUNNING TWO-STROKE ENGINE
DK179952B1 (en) 2018-07-06 2019-10-25 Hans Jensen Lubricators A/S A METHOD FOR UPGRADING A LUBRICATION SYSTEM IN A LARGE SLOW-RUNNING TWO-STROKE ENGINE
EP3623595B1 (de) * 2018-09-11 2021-08-04 Liebherr-Components Colmar SAS Ein verbrennungsmotor
DK180054B1 (en) 2018-10-02 2020-02-11 Hans Jensen Lubricators A/S SUBSTITUTION OF A VALVE SEAT FOR IMPROVING A LUBRICATOR PUMP UNIT AND LUBRICATION SYSTEM OF A LARGE SLOW-RUNNING TWO-STROKE ENGINE, AND AN IMPROVED LUBRICATOR PUMP UNIT
DK180400B1 (en) 2018-10-02 2021-03-30 Hans Jensen Lubricators As Deformation of a valve seat for improving a lubricator pump unit and lubrication system of a large slow-running two-stroke engine
DK181249B1 (en) 2018-10-02 2023-05-31 Hans Jensen Lubricators As Modification of a valve seat for improving a lubricator pump unit and lubrication system of a large slow-running two-stroke engine, and an improved lubricator pump unit
US11668404B2 (en) 2019-04-10 2023-06-06 PAVmed Inc. Systems and methods for a variable flow resistor
DK180390B1 (en) * 2019-06-11 2021-03-05 Hans Jensen Lubricators As Injector for several oils, large engine with such an injector, method of lubrication and use thereof
KR20220015781A (ko) 2020-07-31 2022-02-08 현대중공업 주식회사 선박 엔진의 실린더 오일 측정 장치
DK181120B1 (en) 2021-11-17 2023-01-12 Hans Jensen Lubricators As A large slow-running two-stroke engine, a method of lubricating it and a use of the engine and the method
CN114636088B (zh) * 2022-03-25 2023-08-08 广东精达漆包线有限公司 一种定时定量控制的铜线润滑方法及系统

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KR20200091495A (ko) 2020-07-30
JP6359267B2 (ja) 2018-07-18
DK2722500T3 (en) 2018-11-05
WO2012126473A3 (en) 2012-11-08
RU2638142C2 (ru) 2017-12-11
EP2686527A2 (de) 2014-01-22
WO2012126473A2 (en) 2012-09-27
JP2018066383A (ja) 2018-04-26
CN103939174A (zh) 2014-07-23
SG193531A1 (en) 2013-10-30
JP6682564B2 (ja) 2020-04-15
HK1197094A1 (en) 2015-01-02
RU2586420C2 (ru) 2016-06-10
JP2018109409A (ja) 2018-07-12
RU2013146520A (ru) 2015-04-27
EP2722500A3 (de) 2017-02-15
EP2722500B1 (de) 2018-08-01
KR102247242B1 (ko) 2021-05-03
DK177494B1 (da) 2013-07-15
SG10201809580TA (en) 2018-11-29
EP2722500A2 (de) 2014-04-23
EP2686527B1 (de) 2020-05-06
JP2014508890A (ja) 2014-04-10
DK177258B1 (da) 2012-08-27
CN103534447A (zh) 2014-01-22
RU2013149826A (ru) 2015-05-20
EP3434872B1 (de) 2021-11-10
KR102002181B1 (ko) 2019-07-19
KR102138382B1 (ko) 2020-07-28
DK201270125A (da) 2012-09-19
CN103534447B (zh) 2016-04-20
KR20140010432A (ko) 2014-01-24
JP2014114808A (ja) 2014-06-26
DK2686527T3 (da) 2020-08-17
KR20140004212A (ko) 2014-01-10
CN103939174B (zh) 2017-04-12

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