EP1582706A2 - Brennkraftmaschine mit Zylinderschmiervorrichtung - Google Patents

Brennkraftmaschine mit Zylinderschmiervorrichtung Download PDF

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Publication number
EP1582706A2
EP1582706A2 EP05006988A EP05006988A EP1582706A2 EP 1582706 A2 EP1582706 A2 EP 1582706A2 EP 05006988 A EP05006988 A EP 05006988A EP 05006988 A EP05006988 A EP 05006988A EP 1582706 A2 EP1582706 A2 EP 1582706A2
Authority
EP
European Patent Office
Prior art keywords
lube oil
lubricators
cylinder
oil
electromagnetic valves
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP05006988A
Other languages
English (en)
French (fr)
Other versions
EP1582706B1 (de
EP1582706A3 (de
Inventor
Satoru C/o Nagasaki R&D Center Murata
Sadao KOBE Shipyard & Machinery Works Yoshihara
Tetsuya KOBE Shipyard & Machinery Works Yamamoto
Motoki C/o KOBE Shipyard & Machinery Works Izumi
Takashi TAKASAGO R&D Center Sonoda
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2004108158A external-priority patent/JP3897770B2/ja
Priority claimed from JP2005054678A external-priority patent/JP4402609B2/ja
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP1582706A2 publication Critical patent/EP1582706A2/de
Publication of EP1582706A3 publication Critical patent/EP1582706A3/de
Application granted granted Critical
Publication of EP1582706B1 publication Critical patent/EP1582706B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • 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
    • F01M1/06—Lubricating systems characterised by the provision therein of crankshafts or connecting rods with lubricant passageways, e.g. bores
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/14—Timed lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/18—Other cylinders
    • F02F1/20—Other cylinders characterised by constructional features providing for 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/02—Arrangements of lubricant conduits
    • F01M2011/022—Arrangements of lubricant conduits for lubricating cylinders

Definitions

  • the present invention relates to an internal combustion engine with a cylinder lubricating system applied to a large marine diesel engine, etc., lubricating oil pressure-fed by a lubricating oil pump being accommodated in a common lube oil feeding section, the lubricating oil in the common lube oil feeding section being supplied to a plurality of lubricators attached to engine cylinders to be supplied to the inner surfaces of the cylinders by the system.
  • a plurality of lubricators are arranged along the circumferential direction of the cylinder, a rocker arm is oscillated by a cam formed on a cam shaft driven by the crankshaft of the engine, the plunger of a plunger type oil pump is provided so that an end of which contacts an end of the rocker arm.
  • the plunger of the plunger type oil pump is reciprocated by the rocker arm through the rotation of the cam, and lubricating oil is supplied through an oil pipe connecting the oil pump to each of the lubricators at timing in syntonization with the rotation of the crankshaft to be supplied to the inner surface of the cylinder by the lubricators.
  • lubricating oil is supplied to the inner surface of the cylinder from the lubricators at timing in syntonization with engine rotation, so that the lube oil feed timing and the characteristic of lube oil feed quantity are determined at the stage of engine assembling, the timing and also quantity of oil supplied are difficult to be adjusted, and it is impossible to control the lubrication timing and the quantity of lubricating oil supplied by each of a plurality of lubricators.
  • An object of the invention is to provide an internal combustion engine provided with a cylinder lubricating system, in which it is possible to supply necessary amount of lubricating oil to each of lubricators or to each of positions to be supplied with lubricating oil independently and at necessary timing in order to make it possible to continue normal lube oil feeding even when malfunction occurs in some of the lubricators, and further it is possible to control the timing and amount of oil supply in accordance with varying factors such as actual properties and pressure of lubricating oil, engine load, etc. even during engine operation, and lubricating oil consumption can be reduced.
  • Another object of the invention is to attain lubrication performance capable of meeting increased engine output through evading wear and sticking due to lack of lubricating oil on the inner surface of cylinder by allowing the formation of oil film of uniform thickness spreading through wide range of the inner surface of cylinder, particularly along the axial direction of the cylinder, and to provide a cylinder lubricating system with which lubricating oil consumption can be reduced by eliminating non-effective lubrication.
  • the present invention proposes an internal combustion engine provided with a lubricating system in which lubricating oil pressure-fed by a lubricating oil pump is accommodated in a common lube oil feeding section, the lubricating oil contained in said common lube oil feeding section is supplied to a plurality of lubricators(injectors) through oil passages connecting said common lube oil feeding section to said lubricators and injected to the inner surfaces of cylinders of the engine by said lubricators, wherein are provided a plurality of electromagnetic valves for opening or closing each of said oil passages independently, and a controller for controlling the timing and period of opening of each of said electromagnetic valves independently.
  • the timing and amount of lube oil supply to the inner surface of each cylinder can be adjusted independently in accordance with the lubrication conditions in each cylinder at portions to be supplied with lube oil.
  • said controller controls said electromagnetic valves so that when at least one among two or more of said electromagnetic valves attached per cylinder malfunctions, the opening period of other valve or valves is lengthened.
  • the opening period i. e. the supply amount of lube oil of each of the electromagnetic valves can be controlled independently, so that, when there occurs malfunction in some of the electromagnetic valves, the reduction in the amount of oil supply from lubricators connected to said malfunctioning electromagnetic valves can be complemented by lengthening the opening period of other electromagnetic valves not malfunctioning.
  • lube oil can be supplied to the inner surface of cylinder stably without influenced by the occurrence of malfunction in some of the electromagnetic valves.
  • said controller controls the opening period of said electromagnetic valves so that the amount of oil supply which is determined as a function of the opening period of the electromagnetic valves, or lube oil injection ratio (injection amount of lube oil per hour/engine load or engine output) calculated on the basis of said amount of lube oil supply and engine load, is larger than predetermined minimum amount of lube oil supply or minimum lube oil injection ratio.
  • the amount of lube oil supply is increased by lengthening the opening period of concerned electromagnetic valve when actual amount of lube oil supply or lube oil injection ratio is smaller than the proper value corresponding to engine operating conditions such as engine rotation speed, engine load, etc., and the amount of lube oil supply is decreased by shortening the opening period of concerned electromagnetic valve when actual amount of lube oil supply or lube oil injection ratio is larger than the proper value corresponding to engine operating conditions, so that the most proper amount of lube oil, with which the inner surface of cylinder can be lubricated properly, can be supplied all over the operation range of the engine.
  • an engine rotation speed detector for detecting the rotation speed of the engine and a fuel input sensor for detecting the amount of fuel input calculates engine load on the basis of the engine rotation speed and amount of fuel input detected and controls the opening /closing of said electromagnetic valves so that lube oil is injected from said lubricators every cycle when the engine is operated at a high load higher than a certain load, and once per a few number of cycles when the engine is operated at a low load lower than said certain load, whereby stable lubrication is possible even when necessary amount of lube oil supply per unit time is small, resulting in a reduced lube oil consumption at low load operation(or low speed operation).
  • Said controller calculates lube oil injection ratio (injection amount of lube oil per hour/engine load or engine output) on the basis of the amount of lube oil supply calculated as a function of the opening of the electromagnetic valves and engine load calculated from the detected engine rotation speed and amount of fuel input, and controls the opening period of said electromagnetic valves so that said calculated lube oil injection ratio coincides with a lube oil injection ratio determined beforehand.
  • each of the electromagnetic vales is controlled so that the lube oil injection ratio (the amount of lube oil supply per an hour/engine load or engine output) calculated on the basis of the amount of lube oil supply and detected engine load coincides the targeted lube oil injection ratio, preferably a constant lube oil injection ratio all over the operation range of the engine, so that the amount of lube oil supply can be controlled accurately to supply a minimum amount of lube oil with which the inner surface of cylinder can be lubricated properly in accordance with each operating condition of the engine, and as a result, lube oil consumption can be maintained to a minimum all over the engine operating range.
  • the lube oil injection ratio the amount of lube oil supply per an hour/engine load or engine output
  • a specific gravimeter is provided to said common lube oil feeding section, and said controller controls said electromagnetic valves so that the opening period thereof coincides with a value predetermined in correspondence with the value of specific gravity of lube oil inputted beforehand in the controller from said specific gravimeter or the value of actual specific gravity detected by said specific gravimeter.
  • said controller controls said electromagnetic valves so that the opening timing and period thereof coincides with values predetermined in correspondence with the value of viscosity of lube oil inputted beforehand in the controller from a viscosity meter attached to the common lube oil feeding section or the value of actual viscosity detected by said viscosity meter.
  • the opening period of electromagnetic valve is shortened to evade increase of mass flow due to increased specific gravity by reducing volume flow of lube oil, and the opening period is lengthened to evade decrease of mass flow due to decreased specific gravity by increasing volume flow of lube oil.
  • lube oil supply can be controlled corresponding to the properties of lube oil.
  • a pressure detector or a temperature detector is provided to said common lube oil feeding section, and said controller controls said electromagnetic valves so that the opening period thereof coincides with periods predetermined in correspondence with the pressure or temperature of lube oil in the common lube oil feeding section detected by and inputted from said pressure detector or temperature detector.
  • the opening period of electromagnetic valve is shortened to decrease the amount of lube oil supply as the supply pressure of lube oil in the common lube oil feeding section which is common for each cylinder increases and the opening period of electromagnetic valve is lengthened to increase the amount of lube oil supply as the pressure decreases, so that the amount of lube oil supply can be maintained always to a targeted amount without influenced by lube oil pressure.
  • said controller controls said electromagnetic valves so that the opening period thereof coincides with periods predetermined in correspondence with the lift thereof which is predetermined or measured.
  • the opening period of electromagnetic valve is shortened when the detected lift of electromagnetic valve is larger than the predetermined value or measured value of the lift, and the opening period of electromagnetic valve is lengthened when the detected lift of electromagnetic valve is smaller than the predetermined value or measured value of the lift, so that the amount of lube oil supply can be maintained always to a targeted amount without influenced by the variations of the lift of electromagnetic valve even if the lift varies due to manufacturing errors.
  • said controller controls said electromagnetic valves in correspondence with the predetermined or measured value of the air gap of said electromagnetic valve.
  • the opening period is controlled on the basis of the predetermined or measured air gap between the core and the armature, so that the amount of lube oil supply can be maintained always to a targeted amount without influenced by the variations of the air gap of electromagnetic valve even if the air gap varies due to manufacturing errors.
  • a pressure regulating valve is provided to an end part of the common lube oil feeding section, and the lube oil pump discharges lube oil more than the amount injected to the cylinders of the engine.
  • a return pipe is provided along the common lube oil feeding section, and heat exchange is possible between the lube oil in the common lube oil feeding section and that in the return pipe.
  • the opening area of each of the electromagnetic valves is larger than the sum of the passage area of the lubricators connected to the concerned electromagnetic valve.
  • the present invention proposes a method of supplying lube oil to cylinders in a system in which the lube oil pressure-fed by a lube oil pump is supplied to lubricators attached to a cylinder through electromagnetic valves for adjusting the timing and amount of lube oil supply and oil passages to supply the lube oil to the inner surface of a cylinder in which a piston having a plurality of piston rings reciprocates, wherein lube oil is injected from the lubricators to spaces formed between the piston rings at least once per one reciprocation of piston.
  • the above recited method of supplying lube oil to cylinders is performed by a cylinder lubricating system in which the lube oil pressure-fed by a lube oil pump is supplied to lubricators attached to a cylinder through electromagnetic valves for adjusting the timing and amount of lube oil supply and oil passages to feed the lube oil to the inner surface of a cylinder in which a piston having a plurality of piston rings reciprocates, wherein are provided a crank angle sensor for detecting engine crank angle, rotation speed detector for detecting engine rotation speed, and a load detector for detecting engine load, and a controller for controlling the electromagnetic valves so that lube oil is injected from the lubricators to spaces formed between piston rings at least once per one reciprocation of piston on the basis of the values detected by the crank angle sensor, rotation detector, and load detector.
  • the lube oil injected from the lubricators and pooled in the spaces between piston rings is spread by the reciprocation of the piston in the axial direction on the inner surface of cylinder, and a uniform oil film can be formed in a wide range particularly along the axial direction on the inner surface of cylinder not only near the portion where lube oil is injected from the lubricators.
  • lubrication on the inner surface of cylinder is improved, the occurrence of wear and sticking of piston rings can be evaded, and lubrication performance capable of meeting high-powered engines can be achieved. Also an reduction in lube oil consumption can be achieved by the improvement of lubrication.
  • the firstly injected lube oil injected when the top piston ring is at a position upper than the lubricators is carried upward by the upward travel of the piston to upper portions of the inner surface of the cylinder liner where lubrication condition is severe, and the lube oil injected by the succeeding second lube oil injection from the lubricators and existing in the spaces between piston rings is carried upward along the inner surfaces of the cylinder liner. Therefore, lube oil can spread along the inner surface of cylinder in the axial direction and particularly spreading of lube oil toward upper portions of the inner surface is improved.
  • a first lube oil injection is done when the piston is traveling downward and is at a positioned upper than the lubricator(s) and then a second lube oil injection is done to the spaces between the piston rings in the process of downward traveling of the piston.
  • the firstly injected lube oil injected when the top piston ring is at a position upper than the lubricators is carried downward by the downward travel of the piston to lower portions of the inner surface of the cylinder liner, and the lube oil injected by the succeeding second lube oil injection from the lubricators and existing in the spaces between piston rings is carried downward along the inner surfaces of the cylinder liner. Therefore, lube oil can spread along the inner surface of the cylinder liner in the axial direction and particularly spreading of lube oil toward lower portions of the inner surface is improved.
  • the lubricators are attached to the cylinder such that the injection hole of each of the lubricator directs toward directions circumferential to the inner surface of cylinder so that lube oil is allowed to be injected from the lubricators in directions circumferential to the inner surface of cylinder.
  • lube oil can spread widely in the circumferential direction.
  • the lubricators are arranged in a plurality of rows along the periphery of a cylinder, and lubricators belonging to at least one row are attached to the cylinder such that the injection hole of each of the lubricators directs toward directions circumferential to the inner surface of cylinder so that lube oil is allowed to be injected from the lubricators in directions circumferential to the inner surface of cylinder.
  • lube oil is injected from a plurality of lubricators arranged in a plurality of row in the axial direction of cylinder liner and lube oil injected from lubricators belonging to at least a row is directed to the circumferential direction of the inner surface of cylinder, so that spreading of lube oil in the axial direction is improved and lube oil spread widely also in the circumferential direction on the inner surface of cylinder liner can be improved.
  • FIG.1 is a overall connecting diagram of the first embodiment of the electronic controlled lubricating system of the present invention.
  • reference numeral 11 are cylinder liners and two cylinders liners (cylinders) are shown in the drawing.
  • Reference numerals 12a, 12b, 12c, ⁇ ⁇ ⁇ , 12n are lubricators for feeding lube oil to the inner surface of each cylinder 11.
  • the plural lubricators 12a, 12b, 12c, ⁇ ⁇ ⁇ , 12n are located along the periphery of each cylinder 11 preferably spaced equidistantly.
  • Reference numeral 14 is a lube oil pump
  • 15 is a common lube oil feeding section in which lube oil pressure-fed by the lube oil pump 14 is accumulated.
  • a pressure adjusting valve (not shown in the drawing) is located at an end of the common lube oil feeding section 15, and the lube oil pump 14 feeds the amount of lube oil larger than that supplied for engine lubrication.
  • Reference numerals 16a, 16b, 16c, ⁇ ⁇ ⁇ , 16n are oil passages connecting the common lube oil feeding section 15 to the lubricators 12a, 12b, 12c, ⁇ ⁇ ⁇ , 12n of each cylinder.
  • Reference numerals 17a, 17b, 17c, ⁇ ⁇ ⁇ , 17n are electromagnetic valves provided at each of the lube oil passages 16a, 16b, 16c, ⁇ ⁇ ⁇ , 16n for opening /closing each of the passages 16a, 16b, 16c, ⁇ ⁇ ⁇ , 16n.
  • each of these passages 16a, 16b, 16c, ⁇ ⁇ ⁇ , 16n is controlled by each of the electromagnetic valves independently.
  • Reference numerals 18a, 18b, 18c, ⁇ ⁇ ⁇ , 18n are lube oil flow limiters, each of which are located upstream of each of the electromagnetic valves 17a, 17b, 17c, ⁇ ⁇ ⁇ , 17n which are provided to each of the oil passages 16a, 16b, 16c, ⁇ ⁇ ⁇ , 16n for opening /closing each of the lube oil passages 16a, 16b, 16c, ⁇ ⁇ ⁇ , 16n.
  • FIG.7 is shown the structure of the electromagnetic valve 17(17a, 17b, 17c, 17d, 17e, ⁇ ⁇ ⁇ , 17n) schematically.
  • reference numeral 172 is a valve case
  • 173 is a valve seat
  • 171 is a valve body
  • 174 is an armature fixed on the valve body 171
  • 175 is a solenoid
  • 176 is a valve room.
  • Ga is the air gap between the undersurface of the solenoid 175 and the upper surface of the armature 174 when said lift L is at its maximum.
  • Reference numeral 1 is an engine rotation speed detector for detecting the rotation speed of the engine
  • 2 is a fuel injection quantity sensor for detecting the quantity of fuel injected into the cylinders
  • 3 is a crank angle sensor for detecting crank angles of engine, i.e. rotation positions of the crankshaft of engine.
  • Reference numeral 4 is a load detector by which engine load (output) is calculated from the engine rotation speed detected by said engine rotation speed detector 1 and the fuel injection quantity detected by said fuel injection quantity sensor 2.
  • Reference numeral 21 is oil pressure sensors for detecting the oil pressure of each of said lubricators 12a, 12b, 12c, ⁇ ⁇ ⁇ , 12n.
  • Reference numeral 9 is a specific gravimeter for measuring the specific gravity of the lube oil in the common lube oil feeding section 15 and 10 is a viscosity meter for measuring the viscosity of the lube oil.
  • the engine rotation speed detected by the engine rotation speed detector 1, the engine load detected(calculated) by the load detector 4, the crank angle detected by the crank angle sensor 3, the oil pressures of the lubricators 12a, 12b, 12c, ⁇ ⁇ ⁇ , 12n detected by the oil pressure sensors 21, the specific gravity of lube oil measured by the specific gravimeter 9 and viscosity of lube oil measured by the viscosity meter 10, are inputted to a calculation part 191 (see FIG.2) for calculating timing and period of opening of each electromagnetic valve.
  • measured lift L of each of the electromagnetic valves 17a, 17b, 17c, 17d, 17e, ⁇ ⁇ ⁇ , 17n and measured air gap Ga are also inputted to the calculation part 191 for calculating timing and period of opening of electromagnetic valve.
  • FIG. 2 showing the control block diagram
  • FIG. 1 the operation of the first embodiment will be explained referring to FIG. 2 showing the control block diagram, and FIG. 1.
  • Reference numeral 192 is a setting part of timing and period of opening of each electromagnetic valve, in which target or permissible values of timing and period of opening of each valve corresponding to said detected values are set.
  • the controller 19 performs calculations and controls on the basis of each value detected and the target or permissible values set in the setting part 192 as follows:
  • the calculation part 191 for calculating the timing and period of opening of electromagnetic valve compares the actual amount of lube oil supply, which is calculated as a function of the opening period of electromagnetic valve, or lube oil injection ratio with the minimum amount of lube oil or minimum lube oil injection ratio preset in the opening timing and period setting part 192, and the opening period of each of the electromagnetic valves 17a, 17b, 17c, ⁇ ⁇ ⁇ , 17n is controlled so that lube oil of an amount larger than the minimum amount is supplied or so that lube oil injection ratio is larger than the minimum lube oil injection ratio.
  • the opening period of the concerned electromagnetic valve is lengthened to increase the amount of lube oil to be supplied to the cylinder, and when said actual amount is larger than said minimum value determined corresponding to engine operation conditions, the opening period of the concerned electromagnetic valve is shortened to decrease the amount of lube oil to be supplied to the cylinder, so that an amount of lube oil capable of properly lubricating the inner surface of the cylinder 11 can be supplied always in accordance with engine operating conditions.
  • timing and period of opening setting part 192 are set lube oil feeding modes of feeding lube oil from the lubricator 12a, 12b, 12c, ⁇ ⁇ ⁇ , 12n once per a few number of cycles of engine rotation when the engine is operated under low load lower than a certain reference load and feeding lube oil from the lubricator 12a, 12b, 12c, ⁇ ⁇ ⁇ , 12n for every cycle when the engine is operated under high load higher than a certain reference load.
  • the timing and period of opening calculating part 191 selects a lube oil feeding mode corresponding to the engine rotation speed and engine load inputted from the engine rotation speed detector 1 and load detector 4 respectively from the modes set in the timing and period of opening setting part 192, lube oil is supplied from the lubricators 12a, 12b, 12c, ⁇ ⁇ ⁇ , 12n once per a few number of cycles of engine rotation when the engine is operated under low load lower than a certain reference load, and lube oil is supplied from the lubricators 12a, 12b, 12c, ⁇ ⁇ ⁇ , 12n for every cycle when the engine is operated under high load higher than a certain reference load.
  • lube oil is supplied in accordance with the detected engine load (or engine rotation speed) such that lube oil is supplied for every cycle when operating at a high load(or high rotation speed) with which lubricating condition on the inner surface of cylinder is severe and lube oil is supplied once for a few number of cycles when operating at a low load (or low rotation speed) with which the lubricating condition is not so severe, so that lubricating oil consumption is decreased particularly in low load operation.
  • timing and period of opening setting part 192 is set relations between reference(target) values of engine load(or rotation speed) and lube oil injection ratio(injection amount of lube oil per hour/engine load or engine output) of the amount of the fuel supplied from the lubricators 12a, 12b, 12c, ⁇ ⁇ ⁇ , 12n.
  • the timing and period of opening calculating part 191 calculates lube oil injection ratio on the basis of the actual amount of oil supplied to cylinder and the detected engine load, compares the calculated lube oil injection ratio with the reference(target) value of lube oil injection ratio corresponding to the engine load set in the timing and period of opening setting part 192, and the opening periods of each of the electromagnetic valves 17a, 17b, 17c, ⁇ ⁇ ⁇ , 17n are controlled according to the result of comparison so that the opening period thereof coincides with said reference (target) value.
  • each of the electromagnetic valves 17a, 17b, 17c, ⁇ ⁇ ⁇ , 17n iscontrolled so that the lube oil injection ratio calculated on the basis of actual amount of lube oil supply and detected engine load coincide with reference value of lube oil injection ratio targeted, preferably a constant value, in all over the engine operation conditions, lube oil is accurately controlled to be supplied to the inner surface of the cylinder liner 11 by an amount with which proper lubrication is carried out and lube oil consumption can be reduced to a minimum in all over the operation conditions of the engine.
  • timing and period of opening setting part 192 is set a relation between the lube oil feeding pressure to the cylinder liner 11 and the opening period of the electromagnetic valve, i.e. the amount of lube oil supply.
  • the timing and period of opening calculating part 191 takes out from the timing and period of opening setting part 192 the opening period of each of the electromagnetic valves 17a, 17b, 17c, ⁇ ⁇ ⁇ , 17n corresponding to the detected lube oil feeding pressure in the common lube oil feeding section 15 sent from the pressure sensor 21.
  • timing and period of opening setting part 192 is set a relation between the specific gravity of lube oil and the opening period of the electromagnetic valve, i.e. the amount of lube oil supply such that the opening period is shortened as the specific gravity of lube oil increases and the opening period is lengthened as the specific gravity of lube oil decreases.
  • the timing and period of opening calculating part 191 takes out from the timing and period of opening setting part 192 the opening period of each of the electromagnetic valves 17a, 17b, 17c, ⁇ ⁇ ⁇ , 17n corresponding to the detected specific gravity of lube oil inputted from the specific gravimeter.
  • timing and period of opening setting part 192 is set a relation between the viscosity of lube oil and the timing and period of opening of the electromagnetic valve, i.e. the amount of lube oil supply such that the timing is advanced and the period is lengthened as the viscosity of lube oil increases and the timing is retarded and the period is shortened as the viscosity of lube oil decreases.
  • the timing and period of opening calculating part 191 takes out from the timing and period of opening setting part 192 the timing and period of each of the electromagnetic valves 17a, 17b, 17c, ⁇ ⁇ ⁇ , 17n corresponding to the detected viscosity of lube oil inputted from the viscosity meter.
  • timing and period of opening setting part 192 is set a relation between the lift L of the electromagnetic valve as shown in FIG.7 and the opening period thereof so that the opening period is shortened as the lift L increases in order that the amount of lube oil supply is always constant.
  • the timing and period of opening calculating part 191 takes out from the timing and period of opening setting part 192 the opening period of each of the electromagnetic valves 17a, 17b, 17c, ⁇ ⁇ ⁇ , 17n corresponding to the measured value of lift L.
  • timing and period of opening setting part 192 is set a relation between the air gap Ga of the electromagnetic valve as shown in FIG.7 and the opening period thereof so that the opening period is shortened as the air gap Ga increases in order that the amount of lube oil supply is always constant.
  • the timing and period of opening calculating part 191 takes out from the timing and period of opening setting part 192 the opening period of each of the electromagnetic valves 17a, 17b, 17c, ⁇ ⁇ ⁇ , 17n corresponding to the measured value of air gap Ga.
  • timing and period of opening setting part 192 is set a relation between the sulfur concentration in fuel and the opening period of the electromagnetic valve so that the opening period is determined to allow a minimum amount of lube oil necessary to neutralize the sulfur to flow.
  • the timing and period of opening calculating part 191 takes out from the timing and period of opening setting part 192 the opening period of each of the electromagnetic valves 17a, 17b, 17c, ⁇ ⁇ ⁇ , 17n corresponding to the sulfur concentration in fuel.
  • FIG. 3 to FIG. 5 showing the second to fourth embodiments, a variety of connections between the electromagnetic valves 17 and the lubricators 12 are shown.
  • a plurality of the lubricators 12 are attached to one cylinder as shown by 12a, 12b, 12c, 12d, 12e, ⁇ ⁇ ⁇ , 12n , and oil passages connecting to the lubricators 12 are composed to consist of main passages 161, 162, 163, and 164 and branch oil passages 16a, 16b, 16c, 16d, 16e, ⁇ ⁇ ⁇ , 16n (corresponding to the oil passages in the first embodiment) branching from the main passages 161, 162, 163, and 164 to be connected to each of the lubricators 12a, 12b, 12c, 12d, 12e, ⁇ ⁇ ⁇ , 12n.
  • An electromagnetic valve 17 is provided to each of main oil passages, that is, a valve 17A and a valve 17B are provided to the main oil passages 161, and 162 respectively and another valve 17A and valve 17B are provided to the main oil passages 163 and 164 respectively.
  • a valve 17A and a valve 17B are provided to the main oil passages 161, and 162 respectively
  • another valve 17A and valve 17B are provided to the main oil passages 163 and 164 respectively.
  • Reference numeral 18A is a lube oil flow limiter located upstream of the electromagnetic valve 17A
  • 18B is a lube oil flow limiter located upstream of the electromagnetic valve 17B.
  • the composition other than the points mentioned above is the same as that of the first embodiment shown in FIG.1 and the same component is indicated by the same reference numeral.
  • detectors and sensors shown in FIG. 1 are omitted in FIG.3.
  • the branch oil passages 16a, 16b, 16c, 16d, 16e, ⁇ ⁇ ⁇ , 16n connected to the lubricators 12a, 12b, 12c, 12d, 12e, ⁇ ⁇ ⁇ , 12n arranged along the periphery of one cylinder liner 11 are connected alternately to the main oil passages 161, 162, 163, and 164.
  • the electromagnetic valves 17A and 17B provided to the main oil passages 161 and 162 control respectively the lube oil flow to the alternately disposed lubricators, that is, for example, the valves 17A controls the lubricators 12a, 12c, and 12d, and valves 17B controls the lubricators 12b, 12d, and 12n. By this, controlling of lube oil supply is evened along the circumferential direction of the cylinder.
  • composition other than the points mentioned above is the same as that of the first embodiment shown in FIG.1 or the second embodiment shown in FIG.3 and the same component is indicated by the same reference numeral.
  • detectors and sensors shown in FIG. 1 are omitted in FIG.3.
  • a plurality of the lubricators 12 are attached to one cylinder as shown by 12a, 12b, 12c, 12d, 12e, ⁇ ⁇ ⁇ , 1 2 n
  • oil passages connecting to the lubricators 12 are composed to consist of main passages 161, 162, 163, and 164 and branch oil passages 16a, 16b, 16c, 16d, 16e, ⁇ ⁇ ⁇ , 16n (corresponding to the oil passages in the first embodiment) branching from the main passages 161, 162, 163, and 164 to be connected to each of the lubricators 12a, 12b, 12c, 12d, 12e, ⁇ ⁇ ⁇ , 12n, as is in the case of the second embodiment.
  • a plurality of controllers 19A and 19B instead of a single controller 19 in the second embodiment, and the electromagnetic valves 17A and 17B are controlled independently by the controller 19A, and 19B respectively.
  • composition other than the points mentioned above is the same as that of the first embodiment shown in FIG. 1 or the second embodiment shown in FIG.3 and the same component is indicated by the same reference numeral.
  • detectors and sensors shown in FIG. 1 are omitted in FIG.5.
  • a return pipe 23 and a pressure regulation valve 22 are provided to allow the lube oil in the common lube oil feeding section 15 to return to the lube oil pump 14 so that lube oil temperature in the common lube oil feeding section 15 is even along the widely extending section 15 by heating the lube oil in the common lube oil feeding section 15 by the lube oil in the return pipe 23.
  • composition other than the points mentioned above is the same as that of the first embodiment shown in FIG.1 or the second embodiment shown in FIG.3 and the same component is indicated by the same reference numeral.
  • detectors and sensors shown in FIG. 1 are omitted in FIG.6.
  • the opening area of each of the electromagnetic valves 17(17a, 17b, 17c, ⁇ ⁇ ⁇ , 17n) is larger than the sum of the passage area of the lubricators connected to the concerned electromagnetic valve (for example, In FIG.4, the opening area of the valve 17A is larger than the sum of the passage area of the lubricator 12a, 12b, and 12c) .
  • FIG.8 is an overall schematic representation of the sixth embodiment of the cylinder lubricating system of a diesel engine according to the present invention
  • FIG. 9. is an enlarged detail of a part indicated by Z in FIG.8.
  • reference numeral 11 is a cylinder liner (cylinder)
  • 51 is a piston which reciprocates along the inner surface 11a of the cylinder liner 11
  • 52 are a few number of piston rings received in ring groove of the piston 52 (in the drawing, four rings are provided).
  • Reference numeral 53 are spaces between the piston rings 52 formed between the inner surface of the cylinder liner 11 and the outer surface of the piston 51.
  • Reference numeral 56 is a cylinder cover, 55 is an exhaust valve, and 58 is a combustion chamber.
  • the composition mentioned above is the same as that of prior art.
  • Reference numeral 12 are lubricators (lube oil injectors) for injecting lube oil to the inner surface 11a of the cylinder liner 11.
  • Two lubricators 12 are recognized in the drawing along the axial direction of the cylinder liner 11, and although not shown in the drawing, a plurality of lubricators are arranged along the periphery of the cylinder liner 11.
  • the lubricators 12 are conventional ones used in large diesel engines(detailed explanation is omitted) and they may be arranged in a single row or in three or more rows along the periphery of one cylinder.
  • Reference numeral 14 is a lube oil pump
  • 15 is a common lube oil feeding section where the lube oil pressure-fed by the lube oil pump 14 is accumulated.
  • Reference numeral 156 are oil passages connecting the common lube oil feeding section 15 to the lubricators 12 of each cylinder, 70 are electromagnetic valves provided to each of the oil passages 156 for opening/closing the oil passages 156.
  • Reference numeral 1 is an engine rotation speed detector for detecting the rotation speed of the engine
  • 4 is a load detector for detecting engine load (fuel injection quantity, etc.)
  • 3 is crank angle sensor for detecting crank angles of engine, i.e. rotation positions of the crankshaft of engine .
  • Reference numeral 19 is a controller, to which are inputted the crank angle detected by the crank angle sensor3, the engine rotation speed detected by the engine rotation speed detector 1, and the engine load detected by the load detector 4.
  • the controller 19 controls the timing and period of opening of each of the electromagnetic valves 70 on the basis of those detected values to adjust the timing and quantity of lube oil injection from each of the lubricators(injectors) 12.
  • Each of the electromagnetic valves 70 is controlled independently by the controller 19 to adjust the timing and period of opening thereof.
  • the lube oil pressure-fed by the lube oil pump 14 is accumulated in the common lube oil feeding section 15.
  • the lube oil accumulated in the common lube oil feeding section 15 is supplied to the lubricators 12 through the oil passages 156 and injected to the inner surface of the cylinder liner 11 from each of the lubricators 12.
  • the controller 19 controls the timing and period of opening of each of the electromagnetic valves 70 on the basis of the detected values of crank angle, engine rotation speed, and engine load by the first or second method described in the following.
  • the controlling by the first method is done as follows:
  • the firstly injected lube oil injected when the top piston ring is at a position upper than the lubricators 12 is carried upward by the upward travel of the piston 51 to upper portions of the inner surface of the cylinder liner 11 where lubrication condition is severe, and the lube oil injected by the succeeding second lube oil injection from the lubricators 12 and existing in the spaces 53 between piston rings is carried upward along the inner surfaces of the cylinder liner 11. Therefore, lube oil can spread along the inner surface 11a of the cylinder liner in the axial direction and particularly spreading of lube oil toward upper portions of the inner surface 11a is improved.
  • the controlling by the first method is done as follows:
  • a first lube oil injection is done from the lubricators 12 arranged in two rows when the bottom piston ring(lowermost piston ring of the four piston rings in the drawing) is at a position upper than the lubricators 12(at a position upper than the lower lubricators in the case the lubricators are arranged in two rows as this example), then a second lube oil injection is done in the process of downward travel of the piston 51.
  • a first lube oil injection is done from the lubricators 12 arranged in two rows when the bottom piston ring(lowermost piston ring of the four piston rings in the drawing) is at a position upper than the lubricators 12(at a position upper than the lower lubricators in the case the lubricators are arranged in two rows as this example), then a second lube oil injection is done in the process of downward travel of the piston 51.
  • it is intended to inject lube oil at least to the lowermost space between piston rings, and lube oil is injected to other
  • the firstly injected lube oil injected when the top piston ring is at a position upper than the lubricators 12 is carried downward by the downward travel of the piston 51 to lower portions of the inner surface of the cylinder liner 11 , and the lube oil injected by the succeeding second lube oil injection from the lubricators 12 and existing in the spaces 53 between piston rings is carried downward along the inner surfaces of the cylinder liner 11. Therefore, lube oil can spread along the inner surface 11a of the cylinder liner in the axial direction and particularly spreading of lube oil toward lower portions of the inner surface 11a is improved.
  • the lubricators 12 arranged along the periphery of the cylinder liner 11(arranged in two rows in this example) may be attached to the cylinder such that the injection hole of each of the lubricators is directed to directions circumferential to the inner surface 11a of cylinder liner so that lube oil spreads widely in the circumferential direction of the inner surface 11a of cylinder.
  • the injection hole of lubricators belonging at least to a row may be attached to the cylinder liner 11 such that the injection hole of each of the lubricators is directed to directions circumferential to the inner surface 11a of cylinder liner is directed.
  • lube oil can be spread widely in the circumferential direction of the inner surface 11a of cylinder.
  • lube oil is injected from a plurality of lubricators arranged in a plurality of row in the axial direction of cylinder liner 11 and lube oil injected from lubricators belonging to at leas a row is directed to the circumferential direction of the inner surface of cylinder, so that the spreading of lube oil in the axial direction is improved and lube oil spreads widely also in the circumferential direction on the inner surface 11a of cylinder liner.
  • lube oil is injected from the lubricators 12 to the spaces 53 between piston rings at least once per one reciprocation of the piston 51, and the lube oil pooled in the spaces 53 between piston rings is transferred in the axial direction of the inner surface 11a of cylinder liner, so that an oil film of even thickness is formed on a wide range of the inner surface 11a of cylinder, particularly over a wide range along the axial direction thereof not only near portions where lube oil is injected from the lubricators.
  • the cylinder lubricating system of the present invention it becomes possible to supply lube oil of required amount at required timing to each lubricator, that is, to each portion of the inner surface of cylinder independently, and normal supply of lube oil is possible even when malfunction occurs in some of the lubricators including magnetic valves to open / close the oil passages to supply lube oil to the lubricators. Further, the timing and amount of lube oil supply can be adjusted even in engine operation in accordance with varying factors such as properties of lube oil, lube oil pressure, etc. In addition, lube oil consumption can be reduced.
  • lube oil of required amount at required timing it becomes possible to supply lube oil of required amount at required timing to each lubricator, that is, to each portion of the inner surface of cylinder independently, and supply amount of lube oil or lube oil injection ratio can be controlled so that a minimum amount of lube oil required to maintain good lubricating condition in the inner surface of cylinder to positively evade the occurrence of wear or sticking of piston or piston rings is supplied on the inner surface of cylinder. Therefore, lube oil consumption can be reduced compared with prior art of cylinder lubricating system in which the timing and amount of lube oil supply to a plurality of lubricators are adjusted uniformly not independently.
  • the timing and supply amount or injection ratio of lube oil can be adjusted easily even in engine operation.
  • the lube oil supplied and pooled in the spaces between piston rings is carried in the axial direction on the inner surface of cylinder and an oil film of even thickness is formed on a wide range of the inner surface 11a of cylinder, particularly over a wide range along the axial direction thereof not only near portions where lube oil is injected from the lubricators.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP05006988A 2004-03-31 2005-03-31 Brennkraftmaschine mit Zylinderschmiervorrichtung Not-in-force EP1582706B1 (de)

Applications Claiming Priority (4)

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JP2004108158A JP3897770B2 (ja) 2004-03-31 2004-03-31 シリンダ注油装置を備えた内燃機関
JP2004108158 2004-03-31
JP2005054678 2005-02-28
JP2005054678A JP4402609B2 (ja) 2005-02-28 2005-02-28 シリンダ注油装置

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EP1582706A2 true EP1582706A2 (de) 2005-10-05
EP1582706A3 EP1582706A3 (de) 2005-11-09
EP1582706B1 EP1582706B1 (de) 2008-07-16

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KR (2) KR100750542B1 (de)
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EP2177720A1 (de) * 2008-10-16 2010-04-21 Wärtsilä Schweiz AG Grossdieselmotor
EP2395208A1 (de) 2010-06-11 2011-12-14 Wärtsilä Schweiz AG Grossmotor mit einer Zylinderschmiervorrichtung und Verfahren zur Schmierung eines Zylinders eines Grossmotors
RU2457339C2 (ru) * 2007-05-18 2012-07-27 Ханс Йенсен Лубрикаторс А/С Смазочное устройство и способ дозирования цилиндрового масла
JP2012163098A (ja) * 2011-02-04 2012-08-30 Waertsilae Schweiz Ag シリンダ潤滑デバイス
WO2012126473A3 (en) * 2011-03-18 2012-11-08 Hans Jensen Lubricators A/S Dosing of cylinder lubricating oil into large cylinders
EP2677129A1 (de) * 2009-06-23 2013-12-25 Hans Jensen Lubricators A/S Schmierung von Zylindern von großen Dieselmotoren, wie etwa Schiffsmotoren
KR20140071488A (ko) * 2011-10-12 2014-06-11 가부시키가이샤 아이에이치아이 2사이클 엔진 및 2사이클 엔진의 주유 방법
WO2015144182A1 (en) * 2014-03-25 2015-10-01 Hans Jensen Lubricators A/S Method and system for dosing lubrication oil into cylinders
EP3130771A1 (de) * 2015-08-13 2017-02-15 Winterthur Gas & Diesel AG Schmiervorrichtung für einen zylinderliner, schmierverfahren, sowie zylinderliner
DK201670585A1 (en) * 2016-08-05 2018-01-15 Hans Jensen Lubricators As Safety system for lubrication of the cylinder of a large slow-running internal combustion engine and a large slow-running two-stroke internal combustion engine
CN111156093A (zh) * 2019-12-31 2020-05-15 潍柴动力股份有限公司 柴油-醇类双燃料发动机的控制方法和装置
WO2021213603A1 (en) * 2020-04-22 2021-10-28 Hans Jensen Lubricators A/S Method for lubricating large slow-running marine diesel engines

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WO2012029553A1 (ja) * 2010-09-01 2012-03-08 株式会社Ihi 廃熱発電装置
CN102322309A (zh) * 2011-09-27 2012-01-18 上海北星实业有限公司 一种引擎上的曲轴润滑方法及装置
US9004039B2 (en) * 2012-10-23 2015-04-14 GM Global Technology Operations LLC Cylinder lubrication system
CN103470392B (zh) * 2013-09-30 2015-07-01 庄景阳 点火角度控制汽缸的润滑装置
CN105673244A (zh) * 2013-09-30 2016-06-15 庄景阳 借助离合刹车信号控制汽缸润滑的方法
CN105134327A (zh) * 2013-09-30 2015-12-09 南安市文发电子科技有限公司 活塞同步负压控制润滑孔的控制装置
JP6685864B2 (ja) * 2016-08-29 2020-04-22 三菱重工業株式会社 シリンダ注油装置及びクロスヘッド式内燃機関
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
EP3404224A1 (de) * 2017-05-19 2018-11-21 Winterthur Gas & Diesel AG Schmiervorrichtung für einen grossdieselmotor, verfahren zur zylinderschmierung eines grossdieselmotors, sowie grossdieselmotor
JP7309110B2 (ja) * 2017-12-07 2023-07-18 株式会社三井E&S Du エンジンシステム
JP6973187B2 (ja) * 2018-03-06 2021-11-24 トヨタ自動車株式会社 内燃機関の燃料噴射時期制御装置
CN108343830B (zh) * 2018-03-31 2024-05-28 上汽通用五菱汽车股份有限公司 发动机缸孔润滑装置
JP2022178606A (ja) * 2021-05-20 2022-12-02 株式会社ジャパンエンジンコーポレーション シリンダ注油システム

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EP0509189A1 (de) * 1991-04-18 1992-10-21 Mitsubishi Jukogyo Kabushiki Kaisha Mehrzylinder-Brennkraftmaschine
DE19743955A1 (de) * 1996-10-11 1998-04-16 Man B & W Diesel Gmbh Zylinderschmiervorrichtung für einen Mehrzylinder-Verbrennungsmotor und Verfahren zum Regulieren der Schmierölabgabe
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Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2457339C2 (ru) * 2007-05-18 2012-07-27 Ханс Йенсен Лубрикаторс А/С Смазочное устройство и способ дозирования цилиндрового масла
EP2177720A1 (de) * 2008-10-16 2010-04-21 Wärtsilä Schweiz AG Grossdieselmotor
US8813714B2 (en) 2009-06-23 2014-08-26 Hans Jensen Lubricators A/S Lubrication of cylinders of large diesel engines, such as marine engines
EP2677129A1 (de) * 2009-06-23 2013-12-25 Hans Jensen Lubricators A/S Schmierung von Zylindern von großen Dieselmotoren, wie etwa Schiffsmotoren
EP2395208A1 (de) 2010-06-11 2011-12-14 Wärtsilä Schweiz AG Grossmotor mit einer Zylinderschmiervorrichtung und Verfahren zur Schmierung eines Zylinders eines Grossmotors
JP2012163098A (ja) * 2011-02-04 2012-08-30 Waertsilae Schweiz Ag シリンダ潤滑デバイス
EP3434872A1 (de) * 2011-03-18 2019-01-30 Hans Jensen Lubricators A/S Dosierung von zylinderschmieröl bei grossen zylindern
CN103939174A (zh) * 2011-03-18 2014-07-23 汉斯延森注油器公司 为大型柴油发动机汽缸配给汽缸润滑油的系统和方法
EP2722500A3 (de) * 2011-03-18 2017-02-15 Hans Jensen Lubricators A/S System und Verfahren zur Dosierung von Schmieröl in große Dieselmotorzylinder
RU2638142C2 (ru) * 2011-03-18 2017-12-11 Ханс Йенсен Лубрикейторс А/С Система и способ дозирования смазочного масла для цилиндров в цилиндры больших дизельных двигателей
WO2012126473A3 (en) * 2011-03-18 2012-11-08 Hans Jensen Lubricators A/S Dosing of cylinder lubricating oil into large cylinders
CN103939174B (zh) * 2011-03-18 2017-04-12 汉斯延森注油器公司 为大型柴油发动机汽缸配给汽缸润滑油的系统和方法
KR20140071488A (ko) * 2011-10-12 2014-06-11 가부시키가이샤 아이에이치아이 2사이클 엔진 및 2사이클 엔진의 주유 방법
KR101865407B1 (ko) * 2011-10-12 2018-06-07 가부시키가이샤 아이에이치아이 2사이클 엔진 및 2사이클 엔진의 주유 방법
EP2961951B1 (de) 2014-03-25 2016-11-30 Hans Jensen Lubricators A/S Verfahren und system zur dosierung von schmieröl in zylinder
KR20160134846A (ko) * 2014-03-25 2016-11-23 한스 옌젠 루브리케이터스 에이/에스 실린더에 윤활유를 투여하는 방법 및 시스템
EP2961951A4 (de) * 2014-03-25 2016-02-24 Hans Jensen Lubricators As Verfahren und system zur dosierung von schmieröl in zylinder
WO2015144182A1 (en) * 2014-03-25 2015-10-01 Hans Jensen Lubricators A/S Method and system for dosing lubrication oil into cylinders
EP2961951B2 (de) † 2014-03-25 2019-10-23 Hans Jensen Lubricators A/S Verfahren und system zur dosierung von schmieröl in zylinder
KR102216353B1 (ko) 2014-03-25 2021-02-17 한스 옌젠 루브리케이터스 에이/에스 실린더에 윤활유를 투여하는 방법 및 시스템
EP3130771A1 (de) * 2015-08-13 2017-02-15 Winterthur Gas & Diesel AG Schmiervorrichtung für einen zylinderliner, schmierverfahren, sowie zylinderliner
DK201670585A1 (en) * 2016-08-05 2018-01-15 Hans Jensen Lubricators As Safety system for lubrication of the cylinder of a large slow-running internal combustion engine and a large slow-running two-stroke internal combustion engine
DK179182B1 (en) * 2016-08-05 2018-01-15 Hans Jensen Lubricators As Safety system for lubrication of the cylinder of a large slow-running internal combustion engine and a large slow-running two-stroke internal combustion engine
CN111156093A (zh) * 2019-12-31 2020-05-15 潍柴动力股份有限公司 柴油-醇类双燃料发动机的控制方法和装置
WO2021213603A1 (en) * 2020-04-22 2021-10-28 Hans Jensen Lubricators A/S Method for lubricating large slow-running marine diesel engines
CN115443371A (zh) * 2020-04-22 2022-12-06 汉斯延森注油器公司 用于润滑大型低速运行船用柴油发动机的方法
CN115443371B (zh) * 2020-04-22 2024-05-17 汉斯延森注油器公司 用于润滑大型低速运行船用柴油发动机的方法

Also Published As

Publication number Publication date
DK1582706T3 (da) 2008-09-29
EP1582706B1 (de) 2008-07-16
CN100549369C (zh) 2009-10-14
EP1582706A3 (de) 2005-11-09
CN1676888B (zh) 2010-09-01
DE602005008126D1 (de) 2008-08-28
KR100750542B1 (ko) 2007-08-20
CN101054913A (zh) 2007-10-17
CN1676888A (zh) 2005-10-05
KR20060045405A (ko) 2006-05-17
KR20070041697A (ko) 2007-04-19

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