CN100549369C - Cylinder lubricating system and to the method for cylinder supplying lubricating oil - Google Patents
Cylinder lubricating system and to the method for cylinder supplying lubricating oil Download PDFInfo
- Publication number
- CN100549369C CN100549369C CNB2007101063953A CN200710106395A CN100549369C CN 100549369 C CN100549369 C CN 100549369C CN B2007101063953 A CNB2007101063953 A CN B2007101063953A CN 200710106395 A CN200710106395 A CN 200710106395A CN 100549369 C CN100549369 C CN 100549369C
- Authority
- CN
- China
- Prior art keywords
- lubricant oil
- cylinder
- oil
- lubriator
- piston
- 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.)
- Expired - Fee Related
Links
Images
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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
Abstract
The present invention proposes a kind of internal-combustion engine with cylinder lubricating system and a kind of in system to the method for cylinder supplying lubricating oil, in described system, by the lubricant oil of the pressure feed of lubricating pump by the timing that is used to regulate lubricant oil and supplies with and oil mass solenoid valve and be used for providing the oil duct of lubricant oil to offer a plurality of lubriators on the cylinder that are installed in to the internal surface of cylinder, the piston with a plurality of piston rings in the described cylinder back and forth moves, wherein, piston back and forth operation once sprays lubricant oil from lubriator one time to the gap that is formed between the piston ring at least.Therefore, lubricating on the cylinder surfaces just is improved, and can avoid piston ring that wearing and tearing or bonding take place, and also can obtain to satisfy the greasy property of high output engine demand, and, also can reduce the consumption of lubricant oil by lubricated improvement.
Description
The application is that application number is 200510071619.2, the applying date is on March 31st, 2005, the application people is Mitsubishi Heavy Industry Ltd., denomination of invention dividing an application for the Chinese invention patent application of " internal-combustion engine with cylinder lubricating system ".
Technical field
The present invention relates to a kind of internal-combustion engine that is applied to large-scale marine diesel engine etc. with cylinder lubricating system, lubricant oil by the lubricating pump pressure feed is supplied with in the part in public lubricant oil, by described system, the lubricant oil that described public lubricant oil is supplied with in the part is fed on a plurality of lubriators that are installed on the cylinder, thereby is fed on the internal surface of cylinder.
Background technique
The machinery cylinder lubricating system has been widely used in the large-scale marine diesel engine, wherein, such as patent documentation 1 (day the disclosure utility model application No.59-175619) announcement, a plurality of lubriators are along the circumferential directions of cylinder, and the lubricant oil that the plug type pressure fuel pump that drives by the rotation by bent axle is supplied with is provided for the internal surface of cylinder by means of described lubriator.
In this lubrication system, a plurality of lubriators (sparger) are along the circumferential directions of cylinder, and rocking arm is swung under the driving of the cam that forms on the camshaft that is driven by engine crankshaft, and plunger one end of plug type oil pump contacts with an end of rocking arm.The rotation of the plunger of plug type oil pump by cam be by means of the rocking arm to-and-fro motion, and lubricant oil synchronously offers each lubriator by being connected the oil pipe on the oil pump and the rotation of bent axle, and then offers the internal surface of cylinder by means of these lubriators.In described patent documentation 1 in the disclosed this mechanical cylinder lubricating system, lubricant oil is to offer the internal surface of cylinder with the synchronous timing of engine revolution from lubriator, therefore, the lubricant oil fuel feeding regularly and the feature of lubricant oil fuel delivery be just to have determined in the assembling stage of motor, the timing of fuel feeding and oil mass be difficult to be regulated, and lubricated timing and the oil mass of wanting to control the lubricant oil that is provided by a plurality of lubriators also are impossible.
In the prior art, according to some changing factors, for example to wait the lubricants capacity of controlling supply be impossible for the actual characteristic of lubricant oil, oil pressure, engine load.And when in described a plurality of lubriators some broke down, the lubriator of other normal operation but can not replace the effect of the lubriator that breaks down, therefore, because lubricated state deteriorating, so cylinder surfaces tends to occur wearing and tearing or bonding.
Use prior art the problems referred to above will occur, and be difficult to form one deck and going up in a big way, particularly the oil film that extends along the axial direction of cylinder surfaces.Therefore, very difficult realization can be satisfied the greasy property that growing motor output quantity requires.
And, in the prior art, be difficult to the timing of control to cylinder surfaces jet lubrication oil, that is to say,, be difficult to the position of control piston when the internal surface jet lubrication of cylinder is oily, piston may appear at can not effectively lubricating the position, thereby cause a kind of like this trend, promptly lubrication oil consumption can increase, and weares and teares or adhere to also and can take place the not enough position of lubricant oil distribution on cylinder surfaces.
Summary of the invention
The present invention proposes considering under the situation of above-mentioned problems of the prior art.An object of the present invention is to provide a kind of internal-combustion engine with cylinder lubricating system, in this system, can need provide the position of lubricant oil that the lubricant oil of aequum is provided in the moment that requires to each lubriator or each independently, so that even it is when some lubriator breaks down, still can proceed the normal supply of lubricant oil, even in engine operating state, also can be according to the actual performance and the oil pressure of for example lubricant oil, changing factors such as engine load are controlled the supply timing and the fuel delivery of lubricant oil, and can reduce the consumption of lubricant oil.
Another object of the present invention is, by on the internal surface of cylinder, especially on its axial direction, form the uniform oil film of a layer thickness widely, avoid owing to lacking wearing and tearing and the bonding that lubricant oil causes on the cylinder surfaces, thereby obtain a kind of greasy property that can satisfy the motor output quantity demand of growth, and provide a kind of by eliminating the cylinder lubricating system that ineffective lubrication reduces lubrication oil consumption.
For achieving the above object, the present invention proposes a kind of internal-combustion engine with lubrication system, wherein, by the lubricant oil of lubricating pump pressure feed in public lubricant oil is supplied with part, the lubricant oil that is contained in the described public lubricant oil supply part offers a plurality of lubriators (sparger) by described public lubricant oil is supplied with the oil duct that partly is connected on the described lubriator, and be ejected into by described lubriator on the internal surface of cylinder, wherein, be provided with and a plurality ofly be used for opening independently or closing the solenoid valve of each oil duct and be used for controlling independently the opening timing of each solenoid valve and the controller of endurance.
According to the present invention, owing to be connected to the timing of the solenoid valve on each lubriator and endurance is independent control, so can regulate timing and lubricant oil delivery volume to each cylinder surfaces supplying lubricating oil independently according to the lubrication state of position that will supplying lubricating oil in each cylinder.
Thus, the lubricant oil of aequum can be provided to the position that needs supplying lubricating oil independently in the timing that requires, and the lubricant oil delivery volume can be controlled to minimum value, this minimum value can make the position that each will supplying lubricating oil keep a kind of so good lubrication state, that is, can avoid the generation of wearing and tearing or boning fully.Therefore, compare its lubrication oil consumption with the prior art of cylinder lubricating system and reduce, and in the cylinder lubricating system of prior art, to the fuel feeding of a plurality of lubriators regularly and fuel delivery be unified the adjustment but not independent adjustment.
In the present invention, under the preferable case, described controller is controlled described solenoid valve, thereby when in the two or more solenoid valves on being installed in same cylinder at least one breaks down, just prolongs other one or the unlatching endurance of some valves.
By this structure, can control independently and open the endurance, it is the fuel delivery of each solenoid valve, thereby when some solenoid valve breaks down, by prolonging the unlatching endurance of other solenoid valve that does not break down, compensation is by the minimizing of the fuel delivery that is connected the lubriator generation on the described fault solenoid valve.Thus, can be stably provide lubricant oil, and can not be subjected to breaking down and the influence that brings by some solenoid valve to the internal surface of cylinder.
In the present invention, under the preferable case, described controller is controlled the unlatching endurance of described solenoid valve, thereby making to open described lubricant oil delivery volume that the function of endurance is determined and to spray than (lubricant oil emitted dose/engine load hourly or motor output) according to the lubricant oil that engine load calculates as solenoid valve sprays ratio greater than predetermined minimum lubrication oil supply amount or minimum lubricant oil.
By this structure, when actual lubricant oil delivery volume or lubricant oil spray than less than with the motor operation conditions, engine rotary speed for example, engine load etc., during corresponding appropriate value, just increase the lubricant oil delivery volume by the unlatching endurance that prolongs associated solenoid valve, and when actual lubricant oil delivery volume or lubricant oil spray than greater than the appropriate value corresponding with the motor operation conditions time, then the mode of the unlatching endurance by shortening associated solenoid valve reduces the lubricant oil delivery volume, so just, can provide only lubricant oil delivery volume in the whole service range of motor, the internal surface of cylinder then can obtain suitable lubricating under this only delivery volume.
In the present invention, under the preferable case, be provided with in order to the engine rotary speed detector of detection of engine rotational speed with in order to detect the fuel oil input pickup of fuel oil input quantity, described controller calculates engine load according to detected engine rotary speed and fuel oil input quantity, and control the On/Off of described solenoid valve, make when motor moves under being higher than the high load of specific load, each circulation is all ejected lubricant oil from described lubriator, when under motor is being lower than the low-load of specific load, moving, repeatedly cyclic spray is once oily, even thereby the lubricant oil delivery volume that requires in the time per unit hour, still can carry out stable lubricatedly, realize under the underrun situation minimizing of when low-speed running (or) lubrication oil consumption.
By this structure, the lubricants capacity that lubriator ejects in engine low load (slow-speed of revolution) running hour equally can be according to detected engine load (or engine rotary speed) supplying lubricating oil stably.
The engine load that calculates according to the lubricant oil delivery volume that by the function calculation of opening, by detected engine rotary speed and fuel oil input quantity as solenoid valve, described controller calculates lubricant oil and sprays than (lubricant oil is emitted dose/engine load or motor output per hour), and control unlatching endurance of described solenoid valve, so that the described lubricant oil that calculates sprays than spraying than conforming to predetermined lubricant oil.
By this structure, each solenoid valve is controlled, thereby the feasible lubricant oil that calculates according to lubricant oil delivery volume and detected engine load sprays than (lubricant oil is emitted dose/engine load or motor output per hour) and sprays than conforming to target lube, under the preferable case, in the whole service range of motor, all remain constant lubricant oil and spray ratio, so that the lubricant oil delivery volume can accurately control to the minimum lubrication oil mass, thereby the various operation conditionss according to motor make the internal surface of motor obtain proper lubrication, can also make lubrication oil consumption remain minimum value in the whole service range of motor simultaneously.
In the present invention, under the preferable case, in supplying with partly, described public lubricant oil is provided with pycnometer, and described controller is controlled described solenoid valve, conform to predetermined value so that it opens endurance, this predetermined value with in advance by the value of the proportion of the lubricant oil in the described pycnometer input controller or corresponding by the value of the detected actual specific gravity of described pycnometer.
And, described controller is controlled described solenoid valve, so that its opening timing conforms to predetermined value with the endurance, this predetermined value with supply with lubricating oil viscosity value in the viscosimeter input controller on the part or corresponding by being installed in public lubricant oil in advance by the detected practical viscosity value of described viscosimeter.
By this structure, when using the lubricant oil of big proportion, shorten the unlatching endurance of solenoid valve, by reducing the lubricant oil volume flowrate, avoid causing the increase of mass flow rate owing to the increase of proportion, prolong to open the endurance simultaneously,, avoid reducing to cause reducing of mass flow rate owing to proportion by increasing the lubricant oil volume flowrate.
And, can be by opening timing in advance and the mode that prolongs the unlatching endurance of solenoid valve, prevent because the minimizing of the lubricant oil delivery volume that the viscosity of increase causes, and can avoid the shortage of the lubricant oil that the increase owing to viscosity causes.Therefore, the lubricant oil delivery volume can remain aim parameter, and can not be subjected to the influence of lubricating oil viscosity.
Therefore, by according to lubricants performance, for example proportion and viscosity are come the opening timing and the endurance of control electromagnetic valve, and lubricant oil is supplied with and just can be controlled according to the performance of lubricant oil.
In the present invention, under the preferable case, described public lubricant oil supply unit branch is provided with pressure detector or Temperature Detector, and described controller is controlled described solenoid valve, conform to the institute predetermined time duration so that it opens endurance, described predetermined time duration is corresponding with the lubricating oil pressure or the temperature that are detected by described pressure detector in public lubricant oil supply partly or Temperature Detector and be transfused to.
By this structure, when the lubricant oil supply pressure in the public lubricant oil that is common to each cylinder is supplied with partly increases, can shorten the unlatching endurance of solenoid valve, to reduce the lubricant oil delivery volume, when pressure reduces, then can prolong the unlatching endurance of solenoid valve, to increase the lubricant oil delivery volume, thereby make the lubricant oil delivery volume can remain desired value, and be not subjected to the influence of lubricating oil pressure.
In the present invention, under the preferable case, described controller is controlled described solenoid valve conform to lift institute predetermined time duration so that it opens endurance according to solenoid valve, described predetermined time duration be scheduled to or the lift of detected solenoid valve corresponding.
By this structure, when detected solenoid valve lift during greater than the predetermined value of lift or measured value, can shorten the unlatching endurance of solenoid valve, when detected solenoid valve lift during less than the predetermined value of lift or measured value, can prolong the unlatching endurance of solenoid valve, so that the lubricant oil delivery volume can remain desired value, even the solenoid valve lift is because foozle and when different, also can not be subjected to the influence of described lift difference.
In the present invention, under the preferable case, described controller is controlled described solenoid valve corresponding to the air gap value of described solenoid valve predetermined or that measure.
By this structure, open the endurance according to air clearance control between valve core predetermined or that measure and the armature, thereby make the lubricant oil delivery volume can remain desired value, even the air clearance, also can not be subjected to the influence of difference of the air clearance of solenoid valve because foozle and when different.
In the present invention, the connection between solenoid valve and the lubriator can have following multiple:
(1) each cylinder is provided with a plurality of lubriators, and each described oil duct is connected on each described lubriator, and each described solenoid valve all is arranged on each described oil duct.
(2) each cylinder is provided with a plurality of lubriators, oil leab goes out and a plurality of oil ducts being connected on each described lubriator are formed by a main oil gallery with from described main oil gallery top set, solenoid valve is arranged on the main oil gallery, and single solenoid valve is responsible for lubricant oil is offered a plurality of lubriators.
(3) the oil duct that goes out from each main oil gallery top set is connected on the lubriator that is provided with along the circle alternate of cylinder, therefore, also lubricant oil can be offered other lubriator put along the circumferential ring winding of cylinder that lubriator on being connected the fault solenoid valve even one of them solenoid valve breaks down.
(4) each cylinder is provided with a plurality of lubriators, and is provided with a plurality of controllers in order to control one or more described solenoid valves.
An end of supplying with part at public lubricant oil is provided with pressure regulator valve, and the amount of the lubricant oil that lubricating pump flows out surpasses sprays the oil mass of giving cylinder.Thus, the lubricant oil that public lubricant oil is supplied with in the part can form circulation, and the temperature of the lubricant oil in the public lubricant oil supply part can remain even temperature.
In the present invention, be provided with return tube, thereby can between lubricant oil during public lubricant oil is supplied with partly and the lubricant oil in the return tube, form heat exchange along public lubricant oil supply unit branch.
Thus, raise and the lubricant oil of the described return tube of flowing through can heat public lubricant oil and supplies with lubricant oil in the part by temperature after the pressure regulation, so just, can reduce public lubricant oil and supply with temperature difference between the entrance and exit of part, and the lubricating oil viscosity that public lubricant oil is supplied with in the part evenly distributes along the length direction of this part.
In the present invention, the open area of each solenoid valve is greater than the summation of the aisle spare that is connected in the lubriator on the associated solenoid valve.
Thus, even owing to the difference of valve stroke causes open area difference among a plurality of solenoid valves, still can obtain the lubricant oil delivery volume that requires, and can not be subjected to the influence of the valve stroke difference of solenoid valve by lubriator.
The present invention proposes a kind of method of the cylinder supplying lubricating oil in system, wherein, lubricant oil by the lubricating pump pressure feed offers a plurality of lubriators that are installed on the cylinder by a plurality of solenoid valves and oil duct, wherein solenoid valve is in order to regulate timing and the oil mass that lubricant oil is supplied with, oil duct provides lubricant oil in order to the internal surface to cylinder, the piston that has a plurality of piston rings in the cylinder back and forth moves, wherein the every back and forth operation of piston is once just sprayed lubricant oil from lubriator one time to the gap that is formed between piston ring at least.
Above-mentioned method to the cylinder supplying lubricating oil is carried out by cylinder lubricating system, in this system, lubricant oil by the lubricating pump pressure feed offers a plurality of lubriators that are installed on the cylinder by solenoid valve and oil duct, wherein said solenoid valve is in order to regulate timing and the oil mass that lubricant oil is supplied with, described oil duct provides lubricant oil in order to the internal surface to cylinder, piston with a plurality of piston rings back and forth moves in this cylinder, wherein be provided with crank angle sensor in order to the detection of engine crank angle, rotary speed detector in order to the detection of engine rotational speed, in order to the load detector of detection of engine load and the controller of control electromagnetic valve, thereby when piston whenever back and forth moves one time, according to by crank angle sensor, the detected value of rotary speed detector and load detector is sprayed lubricant oil one time at least from lubriator to the gap that is formed between piston ring.
According to the present invention, because the every back and forth operation of piston once, just to the gap that is formed between the piston ring, spray lubricant oil at least one time from lubriator, so lubricant oil that eject from lubriator and that accumulate in the gap between the piston ring can spread at cylinder surfaces vertically by means of the reciprocal operation of piston, particularly on cylinder surfaces, form the uniform oil film of a layer thickness vertically widely, and not only just form oil film in the place of from lubriator, ejecting near lubricant oil.
Therefore, lubricating on the cylinder surfaces just is improved, and can avoid piston ring that wearing and tearing or bonding take place, and also can obtain to satisfy the greasy property of high output engine demand.And, also can reduce the consumption of lubricant oil by lubricated improvement.
In the present invention, comprise following aspect under the preferable case:
(1) when piston upwards moves and be positioned at the position that is lower than lubriator, carry out lubricant oil injection for the first time, in the process that piston upwards moves, between described piston ring, carry out lubricant oil injection for the second time in the gap then.
By this structure, use first method, when being positioned at the position that is higher than lubriator, the highest piston ring carries out the lubricant oil of injection for the first time, upwards operation by piston upwards is transported to lubrication state more abominable place in top on the interior surface of cylinder liner, by the second time of sending from lubriator subsequently, lubricant oil ejected and be present in lubricant oil in the gap between the piston ring, upwards transported by internal surface along cylinder liner.Therefore, lubricant oil can spread with axial direction along cylinder surfaces, and this especially makes the diffusion of the inside upper surface of lubricant oil be improved.
(2) when piston moves downwards and be positioned at the position that is higher than lubriator (or a plurality of lubriator), carry out lubricant oil injection for the first time, in the process of piston operation downwards, carry out lubricant oil injection for the second time then.
By this structure, when being positioned at the position that is higher than lubriator, the highest piston ring carries out the lubricant oil of injection for the first time, be transported down to the bottom of the internal surface of cylinder liner by the downward operation of piston, and spray by the lubricant oil second time that from lubriator, sends subsequently and be present in lubricant oil in the gap between the piston ring, then transported downwards by internal surface along cylinder liner.Therefore, lubricant oil can spread with axial direction along the internal surface of cylinder liner, and this especially makes lubricant oil be improved to the diffusion of internal surface bottom.
(3) a plurality of lubriators are installed on the cylinder, thereby make the spray-hole of each lubriator be oriented to internal surface around cylinder liner, so that lubricant oil can eject from lubriator along the circumferencial direction of cylinder surfaces.
By this structure, lubricant oil can along the circumferential direction spread widely and come.
(4) lubriator is with many rows' the mode circumferential arrangement along cylinder, and at least one row of lubriator is installed on the cylinder by this way, lubricant oil make the spray-hole of each lubriator be oriented to internal surface, so that can eject from lubriator along the circumferencial direction of cylinder surfaces around cylinder liner.
By this structure, lubricant oil just can be from a plurality of lubriators of arranging in many rows mode axially ejecting along cylinder liner, and the lubricant oil that ejects from least one row's lubriator can be along the circumferencial direction of cylinder surfaces, thereby lubricant oil diffusion vertically is improved, and lubricant oil along the circumferential direction diffusion on the internal surface of cylinder liner is improved.
Description of drawings
Fig. 1 is electronically controlled lubrication first embodiment's of a system of the present invention overall connection diagram.
Fig. 2 is first an embodiment's shown in Figure 1 controlling party block diagram.
Fig. 3 is the connection diagram with corresponding second embodiment of Fig. 1.
Fig. 4 is the connection diagram with corresponding the 3rd embodiment of Fig. 1.
Fig. 5 is the connection diagram with corresponding the 4th embodiment of Fig. 1.
Fig. 6 is the connection diagram with corresponding the 5th embodiment of Fig. 1.
Fig. 7 is the schematic representation of solenoid valve.
Fig. 8 is the general illustration according to the 6th embodiment of diesel engine cylinder lubrication system of the present invention.
Fig. 9 is the amplification detailed view of mark Z indication part among Fig. 8.
Embodiment
Describe the preferred embodiments of the present invention below with reference to accompanying drawings in detail.But should be understood that, unless specifically stated otherwise, otherwise the size of each constituent elements, material, relevant position or the like are as exemplary giving an example among the embodiment, and be not to be the qualification that the scope of the invention is carried out.
Fig. 1 is electronically controlled lubrication first embodiment's of a system of the present invention overall connection diagram.
Referring to Fig. 1, reference character 11 is cylinder liner, and there is shown two cylinder liner (cylinder). Reference character 12a, 12b, 12c..., 12n (omission) are in order to the lubriator to the internal surface supplying lubricating oil of each cylinder 11.A plurality of lubriator 12a, 12b, 12c..., 12n are preferably equidistant distribution along the circumferential arrangement setting of each cylinder 11.
Opening timing and the endurance of each oil duct 16a, 16b, 16 c..., 16n are controlled independently by each solenoid valve.
Reference character 18a, 18b, 18c..., 18n are the flow of lubrication limiters, each oil mass limiter lays respectively at the upstream of each solenoid valve 17a, 17b, 17c..., 17n, these solenoid valves are arranged on each oil leab 16a, 16b, 16c..., the 16n, in order to each oil duct of On/ Off 16a, 16b, 16c..., 16n.
Schematically show among Fig. 7 solenoid valve 17 (17a, 17b, 17c, 17d, 17e ..., 17n) structure.Among this figure, reference character 172 is clack boxes, the 173rd, and valve seat, the 171st, valve body, the 174th, be fixed on the armature on the valve body 171, the 175th, electromagnetic coil, the 176th, valve chamber.In such solenoid valve, when electromagnetic coil 175 energisings, described armature 174 will be pulled upwardly, and 171 of valve bodies can make progress hoist-hole apart from L, and the lubricant oil that supplies in the valve chamber 176 then is sent in the outlet passage 178.Among this figure, Ga is when described lift L is maximum value, the air clearance between the upper surface of the lower surface of electromagnetic coil 175 and armature 174.
In cylinder lubricating system shown in Figure 1, when lubricant oil is supplied with accumulation in the part 15 by lubricating pump 14 pressure feeds and at public lubricant oil, when each oil duct 16a, 16b, 16c..., 16n open down by the driving of each solenoid valve 17a, 17b that is controlled independently by controller 19,17c, 17d, 17e..., 17n simultaneously, the lubricant oil of supplying with accumulation in the part 15 at public lubricant oil just offers each lubriator 12a, 12b, 12c..., 12n by each oil leab 16a, 16b, 16c..., 16n, and then is injected on the internal surface of cylinder liner 11.
The engine rotary speed that detects by engine rotary speed detector 1, by load detector 4 detect the engine load of (calculatings), the oil pressure of the crank angle detected by crank angle sensor 3, the lubriator 12a, the 12b that detect by oil pressure sensor 21,12c..., 12n, the lubricant oil proportion of measuring by pycnometer 9 and all be imported into calculating section 191 (referring to Fig. 2) by the lubricating oil viscosity of viscosimeter 10 measurements, in order to opening timing and the endurance that calculates each solenoid valve.
And, each solenoid valve 17a that measures, 17b, 17c, 17d, 17e ..., the lift L of 17n and the air clearance Ga that measures also be defeated by calculating section 191, in order to opening timing and the endurance that calculates each solenoid valve.
Below, first embodiment's the method for operation will be described referring to the Fig. 2 that shows the controlling party block diagram and Fig. 1.
At first, two lubriators are installed on a cylinder at least, in a plurality of solenoid valves on being connected to a plurality of lubriators at least one (for example 17a) be when having fault, electromagnetic valve part 193 just can prolong other one or more be installed in associated cylinder on unlatching endurance of the valve that is connected of described lubriator.
Because each solenoid valve can be controlled separately, so by this structure, the unlatching endurance of the defective valves by prolonging one or more solenoid valves rather than associated cylinder, make that the minimizing via the fuel delivery that is connected the lubriator on the described defective valves can be compensated by other one or more valves that do not break down.Therefore, even some is connected solenoid valve on a plurality of lubriators that are installed on the cylinder when breaking down, also can provides enough lubricant oil, and can not be subjected to the influence of fault for the internal surface of described cylinder.
And, be used for calculating lubricant oil effective supply amount that the opening timing of solenoid valve and the calculating section of endurance 191 will be calculated as the function of unlatching endurance of solenoid valve or with lubricant oil spray than and the lubricants capacity minimum value that defaults in opening timing and endurance setting section 192 or lubricant oil spray and compare than minimum value, and to each solenoid valve 17a, 17b, 17c..., the unlatching endurance of 17n is controlled, thereby a lubricants capacity greater than described lubricants capacity minimum value is provided, or provides a lubricant oil that sprays than minimum value greater than described lubricant oil to spray ratio.That is to say, when the actual lubricants capacity that provides by some lubriator or its actual ejection than less than the oil mass minimum value or when spraying than minimum value, the unlatching endurance that just each is connected the solenoid valve on these lubriators prolongs, thereby increases the lubricants capacity that offers those lubriators.
By this structure, when actual lubricant oil delivery volume or open lubricant oil that the function of endurance calculated as solenoid valve and spray than the time less than the minimum value determined according to the motor operation conditions, just the unlatching endurance of associated solenoid valve can be prolonged, offer the lubricant oil of cylinder with increase, when described actual amount during greater than the described minimum value of determining according to the motor operation conditions, just the unlatching endurance of associated solenoid valve can be shortened, offer the lubricants capacity of cylinder with minimizing, so just can be all the time provide the internal surface that can make cylinder 11 to obtain the lubricants capacity of proper lubrication according to the operation conditions of motor.
And, in opening timing and endurance setting section 192, when motor is to be lower than when moving under the low-load of specific reference load, then be set at engine cycles and repeatedly just from lubriator 12a, 12b, 12c..., 12n, supply with the lubricant oil supply model of a lubricant oil, when motor is to be higher than when moving under the high load of specific reference load, then be set at the every circulation primary of motor, just from lubriator 12a, 12b, 12c..., 12n, supply the pattern of a lubricant oil.
Opening timing and endurance calculating section 191 are according to engine rotary speed and the engine load imported from engine rotary speed detector 1 and load detector 4 respectively, select a kind of lubricant oil supply model in the pattern from be set in opening timing and endurance setting section 192, when motor is to be lower than when moving under the low-load of specific reference load, then engine cycles is repeatedly just from lubriator 12a, 12b, 12c..., supply with a lubricant oil among the 12n, when motor is to be higher than when moving under the high load of specific reference load, the every circulation primary of motor then is just from lubriator 12a, 12b, 12c..., supply a lubricant oil among the 12n.
By this structure, can be according to detected engine load (or engine rotary speed) supplying lubricating oil, promptly, when the lubrication state of motor on cylinder surfaces is that very abominable high load (or high rotation speed) is down during operation, the every circulation primary of motor is just supplied with lubricant oil one time, when the lubrication state of motor on cylinder surfaces do not have so abominable low-load (or low rotational speed) to move down, then engine cycles is just supplied with lubricant oil several times one time, so just can reduce the consumption of lubricant oil, especially under the underrun situation.
And, in opening timing and endurance setting section 192, be set with engine load (or rotational speed) and spray than the relation between (lubricant oil per hour emitted dose/engine load or motor is exported) with reference to the lubricant oil of (target) value and the amount of fuel from lubriator 12a, 12b, 12c..., 12n, supplied with.
Opening timing and endurance calculating section 191 calculate lubricant oil injection ratio according to the oil mass and the detected engine load of effective supply cylinder, this lubricant oil that calculates is sprayed than being set in lubricant oil injection in opening timing and the endurance setting section 192 and corresponding engine load than comparing with reference to (target) value, and,, it conforms to described reference (target) value so that opening the endurance according to timing and endurance that result relatively controls each solenoid valve 17a, 17b, 17c..., 17n.
Because to each solenoid valve 17a, 17b, 17c..., the feasible lubricant oil that calculates according to the lubricants capacity and the detected engine load of effective supply of the control of the unlatching endurance of 17n sprays and compares the reference value of spraying ratio with target lube, be preferably a constant, under whole motor operation conditions, all conform to, so can be by this structure, lubricant oil is accurately controlled with a such amount, on the internal surface that will supply to cylinder liner 11, the amount of this lubricant oil can make under motor whole service state lubricated suitably carried out and the lubricant oil that is consumed can be reduced to minimum value.
And the supply pressure and the solenoid valve that are set with lubricant oil supply cylinder cover 11 in opening timing and endurance setting section 192 are opened endurance, i.e. relation between the lubricant oil delivery volume.
Opening timing and endurance calculating section 191 take out from opening timing and endurance setting section 192 corresponding to the detected public lubricant oil of sending from pressure transducer 21 and supply with each solenoid valve 17a, 17b of the lubricant oil supply pressure in the part 15, the unlatching endurance of 17c..., 17n.
By this structure, when increasing, oil pressure can reduce the lubricant oil delivery volume by the unlatching endurance that shortens solenoid valve 17a, 17b, 17c..., 17n, and when reducing, oil pressure can increase the lubricant oil delivery volume by the unlatching endurance that prolongs solenoid valve 17a, 17b, 17c..., 17n, the lubricant oil delivery volume just can remain aim parameter like this, and can not be subjected to the influence of lubricating oil pressure.
In opening timing and endurance setting section 192, be set with lubricant oil proportion and solenoid valve and open the endurance, be the relation between the lubricant oil delivery volume, make that when lubricant oil proportion increased, the unlatching endurance promptly shortened, when lubricant oil proportion reduced, the unlatching endurance then prolonged.
Opening timing and endurance calculating section 191 take out the unlatching endurance of each solenoid valve 17a corresponding to the detected lubricant oil proportion of importing, 17b, 17c..., 17n from pycnometer from opening timing and endurance setting section 192.
By this structure, when lubricant oil proportion increases, can reduce the lubricant oil delivery volume by the unlatching endurance that shortens solenoid valve 17a, 17b, 17c..., 17n, it is the volume flowrate of lubricant oil, and when lubricant oil proportion reduces, can increase the lubricant oil delivery volume by the unlatching endurance that prolongs solenoid valve 17a, 17b, 17c..., 17n, the lubricant oil delivery volume just can remain aim parameter like this, and can not be subjected to the influence of lubricant oil proportion.
And, being set with lubricating oil viscosity and solenoid valve in opening timing and endurance setting section 192 opens regularly and the endurance, it is the relation between the lubricant oil delivery volume, feasible timing advance and endurance prolongation when lubricating oil viscosity increases, definite time delay and endurance shorten when lubricating oil viscosity reduces.
Opening timing and endurance calculating section 191 take out timing and the endurance of each solenoid valve 17a corresponding to the detected lubricating oil viscosity of importing, 17b, 17c..., 17n from viscosimeter from opening timing and endurance setting section 192.
By this structure, can be by shifting to an earlier date the decline that opening timing prevents to increase owing to viscosity the greasy property that causes, described opening timing in advance can make the lubricant oil delivery volume increase, and can prevent that because viscosity increases the decline of the greasy property that causes, the unlatching endurance of described prolongation solenoid valve can make to the endurance of the internal surface supplying lubricating oil of cylinder liner 11 and prolong by the unlatching endurance that prolongs solenoid valve 17a, 17b, 17c..., 17n.Thereby the lubricant oil delivery volume can remain aim parameter.
In opening timing and endurance setting section 192, be set with as shown in Figure 7 solenoid valve lift L and the relation of solenoid valve between the unlatching endurance, make when lift L increases, open the endurance shortening, so that the lubricant oil delivery volume is always constant.
Opening timing and endurance calculating section 191 take out the unlatching endurance of each solenoid valve 17a corresponding to the lift range value L that measures, 17b, 17c..., 17n from opening timing and endurance setting section 192.
By this structure, when the measured load of lift L during greater than the setting value of lift L, can shorten the unlatching endurance of solenoid valve 17a, 17b, 17c..., 17n, when the measured load of lift L during less than the setting value of lift L, then can prolong and open the endurance, like this, have difference even cause owing to foozle in the lift range value of these solenoid valves, the lubricant oil delivery volume also can remain aim parameter, and can not be subjected to the influence of described error.
In opening timing and endurance setting section 192, be set with the air clearance Ga and the relation of solenoid valve between the unlatching endurance of solenoid valve as shown in Figure 7, make when air clearance Ga increases, open the endurance shortening, so that the lubricant oil delivery volume is always constant.
Opening timing and endurance calculating section 191 take out the unlatching endurance of each solenoid valve 17a corresponding to measured air clearance Ga, 17b, 17c..., 17n from opening timing and endurance setting section 192.
By this structure, when the measured load of air clearance Ga during greater than the setting value of air clearance Ga, can shorten the unlatching endurance of solenoid valve 17a, 17b, 17c..., 17n, when the measured load of air clearance Ga during less than the setting value of air clearance Ga, can prolong and open the endurance, like this, have difference even cause owing to foozle in the air clearance of these solenoid valves, the lubricant oil delivery volume also can remain aim parameter, and can not be subjected to the influence of described error.
In opening timing and endurance setting section 192, be set with sulphur concentration in the fuel and solenoid valve and open relation between the endurance, make the described unlatching endurance determined with allow in order in and the minimum lubrication oil flow that requires of sulphur in the fuel flow through.
Opening timing and endurance calculating section 191 take out the unlatching endurance of each solenoid valve 17a corresponding to the sulphur concentration in the fuel, 17b, 17c..., 17n from opening timing and endurance setting section 192.
By this structure, the unlatching endurance that can be by control electromagnetic valve 17a, 17b, 17c..., 17n and keep in order in and the minimum lubrication oil flow that requires of sulphur in the fuel suppress the increase of sulphur, the increase of this sulphur can make the lubrication circumstances on the cylinder surfaces degenerate.
Showing second to Fig. 3 to Fig. 5 of the 4th embodiment, showing the multiple annexation between solenoid valve 17 and the lubriator 12.
In second embodiment shown in Figure 3, a plurality of as among the figure by reference character 12a, 12b, 12c, 12d, 12e ..., the lubriator 12 shown in the 12n is installed on the cylinder, be connected on the lubriator 12 oil duct by main oil gallery 161,162,163,164 and go out from main oil gallery 161,162,163,164 top sets, with each lubriator 12a, 12b, 12c, 12d, 12e ..., oil duct 16a, the 16b that are connected of 12n, 16c, 16d, 16e ..., 16n (corresponding to the oil duct among first embodiment) forms.All be provided with solenoid valve 17 on each main oil gallery, that is to say, solenoid valve 17A and solenoid valve 17B are separately positioned on main oil gallery 161 and 162, and another solenoid valve 17A and solenoid valve 17B are separately positioned on main oil gallery 163 and 164.Therefore, can control a plurality of lubriators 12 by means of a solenoid valve 17, and then can reduce the quantity of solenoid valve 17.
By the way, detector shown in Fig. 1 and sensor in Fig. 3, have been omitted.
In the 3rd embodiment shown in Figure 4, be connected each lubriator 12a of being provided with along the circumferential arrangement of cylinder liner 11,12b, 12c, 12d, 12e ..., oil duct 16a, 16b on the 12n, 16c, 16d, 16e ..., 16n alternately is connected on the main oil gallery 161,162,163,164.The solenoid valve 17A and the 17B that are arranged on main oil gallery 161 and 162 control flow of lubricant respectively in the lubriator of arranged alternate, that is to say, for example, and valve 17A control lubriator 12a, 12c and 12d, valve 17B then controls lubriator 12b, 12d and 12n.Thus, the control of supplying with along the lubricant oil of the circumferencial direction of cylinder is uniform.
Except the premises, this formation and first embodiment shown in Figure 1 or second embodiment's shown in Figure 3 is identical, and components identical is represented by identical reference character.
By the way, detector shown in Fig. 1 and sensor in Fig. 3, have been omitted.
In the 4th embodiment shown in Figure 5, a plurality of as among the figure by reference character 12a, 12b, 12c, 12d, 12e, ..., lubriator 12 shown in the 12n is installed on the cylinder, be connected oil duct on the lubriator 12 by main oil gallery 161,162,163,164 and from main oil gallery 161,162,163,164 top sets go out, with each lubriator 12a, 12b, 12c, 12d, 12e, ..., the oil duct 16a that 12n is connected, 16b, 16c, 16d, 16e, ..., 16n (corresponding to the oil duct among first embodiment) forms, and is the same with situation among second embodiment.In this 4th embodiment, a plurality of controller 19A and 19B have replaced the single controller 19 among second embodiment, and solenoid valve 17A and 17B are controlled independently by controller 19A and 19B respectively.
Except the premises, this formation and first embodiment shown in Figure 1 or second embodiment's shown in Figure 3 is identical, and components identical is represented by identical reference character.
By the way, detector shown in Fig. 1 and sensor in Fig. 5, have been omitted.
In the 5th embodiment shown in Figure 6, be provided with return tube 23 and pressure regulator valve 22, with so that the lubricant oil that public lubricant oil is supplied with in the part 15 be back in the lubricating pump 14, like this, by heat the lubricant oil in the public lubricant oil supply part 15 by means of the lubricant oil in the return tube 23, the lubricating oil temperature that public lubricant oil is supplied with in the part 15 is uniformly along the part 15 of extensively extending.
Except the premises, this formation and first embodiment shown in Figure 1 or second embodiment's shown in Figure 3 is identical, and components identical is represented by identical reference character.
By the way, detector shown in Fig. 1 and sensor in Fig. 6, have been omitted.
In each embodiment, each solenoid valve 17 (17a, 17b, 17c ... open area 17n) is all greater than the summation of the aisle spare that is connected the lubriator on the associated solenoid valve (for example, in Fig. 4, the open area of solenoid valve 17A is greater than the summation of the aisle spare of lubriator 12a, 12b and 12c).
Thus, even owing to the difference of valve stroke causes that the open area among a plurality of solenoid valves changes, the lubricant oil delivery volume of the lubriator of flowing through that still can obtain to require, and can not be subjected to the influence of difference of the valve stroke of solenoid valve.
Fig. 8 is the described general illustration of the 6th embodiment according to diesel engine cylinder lubrication system of the present invention, and Fig. 9 is the amplification detailed view of mark Z indication part among Fig. 8.
In Fig. 8 and Fig. 9, reference character 11 is cylinder liner (cylinders), the 51st, and along the internal surface 11a pistons reciprocating of cylinder liner 11, the 52nd, some are contained in the piston ring (being provided with four piston rings among the figure) in the annular groove of piston 52.Reference character 53 is the gaps between the piston ring 52, and this gap is formed between the outer surface of the internal surface of cylinder liner 11 and piston 51.Reference character 56 is cylinder head, the 55th, and outlet valve, the 58th, firing chamber.Said structure is identical with structure of the prior art.
Each solenoid valve 70 is independently by controller 19 controls, to adjust its opening timing and endurance separately.
When the diesel engine that is provided with when the mode with the 5th embodiment is in running state, supply with accumulation in the part 15 at public lubricant oil by the lubricant oil of the pressure feed of lubricating pump 14.When each oil duct 156 is opened by each solenoid valve 70 of being controlled independently by controller 19 respectively, the lubricant oil of supplying with accumulation in the part 15 at public lubricant oil just offers lubriator 12 by oil duct 156, and sprays to the internal surface of cylinder liner 11 from each lubriator 12.
First kind of controlling method carried out as follows:
When piston 51 upwards moves, when being positioned at the position that is higher than lubriator 12, (as this embodiment, arranges under the situation of setting in the highest piston ring (shown in the figure four piston ring 52 in uppermost that piston ring) in two rows' modes at lubriator, be positioned at and be higher than the position of arranging lubriator) time, just from lubriator 12, carry out lubricant oil injection for the first time, in the process that piston 51 upwards moves, carry out lubricant oil injection for the second time then.Owing between piston ring, have three gaps 53 among this embodiment, therefore, be contemplated at least to the gap of the top between piston ring jet lubrication oil, and in the lubriator that is provided with by means of the modes with two rows any one is to other gap jet lubrication oil between piston ring.
By described first method, when being positioned at the position that is higher than lubriator 12, (as this embodiment, arranges under the situation of setting in the highest piston ring in two rows' mode at lubriator, be positioned at and be higher than the position of arranging lubriator) time lubricant oil that for the first time of carrying out sprays, move the more abominable top of lubrication state on the internal surface that upwards is transported to cylinder liner 11 by making progress of piston 51, and by lubricant oil ejects the second time of sending from lubriator 12 subsequently, and be present in the lubricant oil in the gap 53 between the piston ring, then upwards transported by internal surface along cylinder liner 11.Therefore, lubricant oil can spread with axial direction along the internal surface 11a of cylinder liner, and has improved the diffusion of lubricant oil to the top of internal surface 11a especially.
Second kind of controlling method carried out as follows:
When piston 51 operation downwards, be higher than lubriator 12 and (as this embodiment, arrange under the situation of setting when the piston ring of bottom (shown in the figure four piston ring in nethermost that piston ring) is positioned in two rows' modes at lubriator, it is positioned at and is higher than the down position of row's lubriator) the position time, just from lubriator 12, carry out lubricant oil injection for the first time, in the processes of piston 51 operation downwards, carry out lubricant oil injection for the second time then.Owing between piston ring, have three gaps 53 among this embodiment, therefore, be contemplated at least to the gap jet lubrication oil bottom between piston ring, and in the lubriator that is provided with by means of the modes with two rows any one is to other gap jet lubrication oil between piston ring.
Pass through second method, when being positioned at the position that is higher than lubriator 12, (as this embodiment, arranges under the situation of setting in the piston ring of bottom in two rows' modes at lubriator, be positioned at and be higher than the down position of row's lubriator) time lubricant oil that for the first time of carrying out sprays, be transported down to the bottom of the internal surface of cylinder liner 11 by the downward operation of piston 51, and spray by the lubricant oil second time that from lubriator 12, sends subsequently and be present in lubricant oil in the gap 53 between the piston ring, then transported downwards by internal surface along cylinder liner 11.Therefore, lubricant oil can spread with axial direction along the internal surface 11a of cylinder liner, and has improved the diffusion of lubricant oil to internal surface 11a bottom especially.
When lubriator 12 in many rows' (being two rows among this embodiment) mode when the circumferential arrangement of cylinder liner 11 is provided with, the spray-hole of at least one row's lubriator can be installed on the cylinder liner 11, makes the spray-hole of each lubriator point to the circumferencial direction of interior surface of cylinder liner.In this case, lubricant oil also can spread widely along the circumferencial direction of the internal surface 11a of cylinder.
Thus, lubricant oil just can be from the lubriator of arranging setting in many rows mode axially ejecting along cylinder liner 11, and the lubricant oil that ejects from least one row's lubriator then can be directed to the circumferencial direction of interior surface of cylinder liner, like this, lubricant oil diffusion vertically just can improve, and lubricant oil can also spread widely along the circumferencial direction of the internal surface 11a of cylinder liner.
According to the 6th embodiment, piston 51 every back and forth operations once, lubricant oil just sprays once from the gap 53 of lubriator 12 between piston ring at least, and the lubricant oil that accumulates in the gap 53 between the piston ring will moving axially along the internal surface 11a of cylinder liner, like this will be on the internal surface 11a of cylinder, especially on its axial direction, form the uniform oil film of a layer thickness widely, and not only just form oil film in the place of from lubriator, ejecting near lubricant oil.
Thus, lubricating on the internal surface 11a of cylinder liner just is improved, and the situation that can avoid piston ring 52 wearing and tearing to take place or adhere to.And, because lubriator 12 improves the consumption that has also reduced lubricant oil.
As previously mentioned, according to cylinder lubricating system of the present invention, can be independently to each lubriator under the timing that requires, the lubricant oil of required amount promptly is provided to the various piece of cylinder surfaces, even some comprises when the lubriator of solenoid valve breaks down, still can be lubricated the normal supply of oil; Described solenoid valve opens/cuts out the oil duct to these lubriator supplying lubricating oils.And, even in the running state of motor, still can regulate lubricant oil and supply with regularly and delivery volume according to for example changing factor such as lubricants performance, lubricant oil oil pressure.In addition, also can reduce the consumption of lubricant oil.
And, according to the present invention, can be in the timing that requires independently to each lubriator, the lubricant oil of required amount promptly is provided to the various piece of cylinder surfaces, and lubricant oil delivery volume or lubricant oil sprays than can controlling, and can keep cylinder surfaces good lubrication condition and can avoid piston or piston ring to take place to wear and tear or the desired minimum lubrication oil mass that bonds again thereby provide on cylinder surfaces.Therefore, compare its lubrication oil consumption with the prior art of cylinder lubricating system and reduce, in the cylinder lubricating system of prior art, need to adjust uniformly regularly and, but not adjust independently to the amount of a plurality of lubriator supplying lubricating oils.
Even in the running state of motor, also can adjust the injection timing and the delivery volume of lubricant oil at an easy rate or spray ratio.
And, according to the present invention, because the every back and forth operation of piston once, just to the gap between piston ring, spray lubricant oil at least one time from lubriator, so the lubricant oil that provides and accumulate in the gap between the piston ring is transported on the cylinder surfaces with axial direction, and on the internal surface 11a of cylinder, especially on its axial direction, can form the uniform oil film of a layer thickness widely, and not only just form oil film in the place of from lubriator, ejecting near lubricant oil.
Thus, lubricating on the internal surface of cylinder liner just is improved, and can avoid piston ring that the situation of wearing and tearing or bonding takes place.And, so because lubricated being improved also reduced the consumption of lubricant oil.
Claims (6)
1, a kind of in system to the method for cylinder supplying lubricating oil, in described system, by the lubricant oil of the pressure feed of lubricating pump by the timing that is used to regulate lubricant oil and supplies with and oil mass solenoid valve and be used for internal surface to cylinder and provide the oil duct of lubricant oil to offer two or more to be installed in a lubriator on the cylinder, the piston with a plurality of piston rings in the described cylinder back and forth moves, it is characterized in that, piston back and forth operation once sprays lubricant oil from lubriator one time to the gap that is formed between the piston ring at least.
2, the method to the cylinder supplying lubricating oil according to claim 1, wherein, when piston upwards moved and be positioned at the position that is lower than lubriator, carrying out for the first time, lubricant oil sprayed, in the process that piston upwards moves, lubricant oil is injected in the middle gap of piston ring for the second time then.
3, the method to the cylinder supplying lubricating oil according to claim 1, wherein, when piston moved downwards and be positioned at the position that is higher than lubriator, carrying out for the first time, lubricant oil sprayed, in the process of piston operation downwards, lubricant oil is injected in the middle gap of piston ring for the second time then.
4, the method to the cylinder supplying lubricating oil according to claim 1, wherein, lubriator is installed on the described cylinder like this, make the spray-hole of each lubriator be oriented to direction, thereby lubricant oil can eject along the circumferencial direction of cylinder surfaces from lubriator around interior surface of cylinder liner.
5, the method to the cylinder supplying lubricating oil according to claim 1, wherein, lubriator is with the circumferential arrangement setting along cylinder of many rows' mode, and at least one row of lubriator is installed on the cylinder by this way, make the spray-hole of each lubriator be oriented to internal surface direction, thereby lubricant oil can eject along the circumferencial direction of cylinder surfaces from lubriator around cylinder liner.
6, a kind of cylinder lubricating system, wherein the lubricant oil by the lubricating pump pressure feed offers a plurality of lubriators that are installed on the cylinder by a plurality of solenoid valves and oil duct, wherein said solenoid valve is used to regulate timing and the oil mass that lubricant oil is supplied with, described oil duct then is used for providing lubricant oil to the internal surface of cylinder, the piston with a plurality of piston rings in described cylinder back and forth moves, wherein, be provided with crank angle sensor in order to the detection of engine crank angle, in order to the rotary speed detector of detection of engine rotational speed and the load detector of loading in order to detection of engine, with controller in order to control electromagnetic valve, thereby according to by crank angle sensor, the detected value of rotary speed detector and load detector, when piston whenever back and forth moves one time, to the gap that is formed between the piston ring, spray lubricant oil at least one time from described lubriator.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004108158A JP3897770B2 (en) | 2004-03-31 | 2004-03-31 | Internal combustion engine with cylinder lubrication device |
| JP108158/04 | 2004-03-31 | ||
| JP2005054678A JP4402609B2 (en) | 2005-02-28 | 2005-02-28 | Cylinder lubrication device |
| JP054678/05 | 2005-02-28 |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2005100716192A Division CN1676888B (en) | 2004-03-31 | 2005-03-31 | Internal combustion engine with cylinder lubricating system and method for supplying lubricant oil to cylinder |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101054913A CN101054913A (en) | 2007-10-17 |
| CN100549369C true CN100549369C (en) | 2009-10-14 |
Family
ID=34889462
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2007101063953A Expired - Fee Related CN100549369C (en) | 2004-03-31 | 2005-03-31 | Cylinder lubricating system and to the method for cylinder supplying lubricating oil |
| CN2005100716192A Expired - Fee Related CN1676888B (en) | 2004-03-31 | 2005-03-31 | Internal combustion engine with cylinder lubricating system and method for supplying lubricant oil to cylinder |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2005100716192A Expired - Fee Related CN1676888B (en) | 2004-03-31 | 2005-03-31 | Internal combustion engine with cylinder lubricating system and method for supplying lubricant oil to cylinder |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP1582706B1 (en) |
| KR (2) | KR100750542B1 (en) |
| CN (2) | CN100549369C (en) |
| DE (1) | DE602005008126D1 (en) |
| DK (1) | DK1582706T3 (en) |
Families Citing this family (25)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DK176934B1 (en) * | 2007-05-18 | 2010-05-31 | Hans Jensen Lubricators As | Lubrication apparatus and method for dosing cylinder lubricating oil |
| DK2177720T3 (en) * | 2008-10-16 | 2014-06-30 | Wärtsilä Schweiz AG | Large diesel engine |
| DK177746B1 (en) * | 2009-06-23 | 2014-05-26 | Hans Jensen Lubricators As | Process for cylinder lubrication of large diesel engines such as ship engines |
| EP2395208A1 (en) * | 2010-06-11 | 2011-12-14 | Wärtsilä Schweiz AG | Large motor with a cylinder lubrication device and method for lubricating a cylinder of a large motor |
| WO2012029553A1 (en) * | 2010-09-01 | 2012-03-08 | 株式会社Ihi | Waste heat power generator |
| DK2484875T3 (en) * | 2011-02-04 | 2014-02-24 | Waertsilae Nsd Schweiz Ag | Cylinder lubrication device |
| DK177258B1 (en) * | 2011-03-18 | 2012-08-27 | Hans Jensen Lubricators As | Dosing system for cylinder lubricating oil for large cylinders and method for dosing cylinder lubricating oil for large cylinders |
| CN102322309A (en) * | 2011-09-27 | 2012-01-18 | 上海北星实业有限公司 | Method and device for lubricating crank shaft on engine |
| JP5933217B2 (en) * | 2011-10-12 | 2016-06-08 | 株式会社Ihi | Two-cycle engine and method of lubricating two-cycle engine |
| US9004039B2 (en) * | 2012-10-23 | 2015-04-14 | GM Global Technology Operations LLC | Cylinder lubrication system |
| CN103470392B (en) * | 2013-09-30 | 2015-07-01 | 庄景阳 | Lubricating device for ignition angle control cylinder |
| CN105673244A (en) * | 2013-09-30 | 2016-06-15 | 庄景阳 | Method for controlling cylinder lubrication by aid of clutch brake signals |
| CN105134327A (en) * | 2013-09-30 | 2015-12-09 | 南安市文发电子科技有限公司 | Control device for synchronous negative pressure control over lubricating hole through piston |
| EP2961951B2 (en) * | 2014-03-25 | 2019-10-23 | Hans Jensen Lubricators A/S | Method and system for dosing lubrication oil into cylinders |
| EP3130771A1 (en) * | 2015-08-13 | 2017-02-15 | Winterthur Gas & Diesel AG | Lubricator for a cylinder liner, lubrication method, and cylinder liner |
| 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 |
| JP6685864B2 (en) * | 2016-08-29 | 2020-04-22 | 三菱重工業株式会社 | Cylinder lubrication device and crosshead internal combustion engine |
| CN106567960B (en) * | 2016-10-17 | 2019-07-05 | 潍柴动力股份有限公司 | A kind of control method and system of solenoid valve |
| EP3404224A1 (en) * | 2017-05-19 | 2018-11-21 | Winterthur Gas & Diesel AG | Lubricating device for a large diesel motor, method for cylinder lubrication of a large diesel engine and large diesel engine |
| JP7309110B2 (en) * | 2017-12-07 | 2023-07-18 | 株式会社三井E&S Du | engine system |
| JP6973187B2 (en) * | 2018-03-06 | 2021-11-24 | トヨタ自動車株式会社 | Fuel injection timing control device for internal combustion engine |
| CN108343830B (en) * | 2018-03-31 | 2024-05-28 | 上汽通用五菱汽车股份有限公司 | Engine cylinder hole lubricating device |
| CN111156093B (en) * | 2019-12-31 | 2023-01-06 | 潍柴动力股份有限公司 | Control method and device for diesel-alcohol dual-fuel engine |
| CN115443371B (en) * | 2020-04-22 | 2024-05-17 | 汉斯延森注油器公司 | Method for lubricating large low-speed marine diesel engine |
| JP2022178606A (en) * | 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 | Cylinder oil-filling system |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ES506543A0 (en) * | 1980-10-04 | 1982-08-16 | British Petroleum Co | A LUBRICATING SYSTEM FOR AN INTERNAL COMBUSTION ENGINE CYLINDER |
| JPS6045710A (en) | 1983-08-23 | 1985-03-12 | Nachi Fujikoshi Corp | Diesel engine lubrication device |
| DK171974B1 (en) * | 1988-11-01 | 1997-09-01 | Mitsubishi Heavy Ind Ltd | Lubricator for a cylinder in an internal combustion engine |
| JPH02135612U (en) * | 1989-04-14 | 1990-11-13 | ||
| JPH04318253A (en) * | 1991-04-18 | 1992-11-09 | Mitsubishi Heavy Ind Ltd | Multicylinder engine |
| DK173288B1 (en) * | 1996-10-11 | 2000-06-13 | Man B & W Diesel As | Cylinder lubrication unit for a multi-cylinder internal combustion engine and method for controlling the amount of delivery from a cylinder |
| PL198331B1 (en) * | 1998-11-05 | 2008-06-30 | Hans Jensen Lubricators As | Method of lubrication of cylinders for heavy diesel engines and diesel engine with cylinder wall lubrication system for implementing the method |
| DK173533B1 (en) | 1999-01-18 | 2001-02-05 | Man B & W Diesel As | Method of lubricating a cylinder in an internal combustion engine as well as cylinder lubrication system and connecting element |
| DE19959309A1 (en) | 1999-12-09 | 2001-06-21 | Man B & W Diesel As Kopenhagen | Engine has switching valves next to lubricant outlets with which supply lines can be blocked or opened at times determined by controller from lubricant demand derived from measurements |
| DE19959300A1 (en) | 1999-12-09 | 2001-06-21 | Man B & W Diesel As Kopenhagen | Engine has lubricant ejection devices of constant capacity and frequency of ejection processes is varied to vary quantity of lubricant delivered to cylinder surface |
| DE60118589T2 (en) * | 2000-10-24 | 2007-05-16 | Hans Jensen Lubricators A/S | DOSING |
| JP3806398B2 (en) * | 2002-11-28 | 2006-08-09 | 三菱重工業株式会社 | Cylinder lubrication device |
| JP3897770B2 (en) | 2004-03-31 | 2007-03-28 | 三菱重工業株式会社 | Internal combustion engine with cylinder lubrication device |
-
2005
- 2005-03-31 CN CNB2007101063953A patent/CN100549369C/en not_active Expired - Fee Related
- 2005-03-31 DK DK05006988T patent/DK1582706T3/en active
- 2005-03-31 DE DE602005008126T patent/DE602005008126D1/en active Active
- 2005-03-31 KR KR1020050027386A patent/KR100750542B1/en active IP Right Grant
- 2005-03-31 EP EP05006988A patent/EP1582706B1/en not_active Not-in-force
- 2005-03-31 CN CN2005100716192A patent/CN1676888B/en not_active Expired - Fee Related
-
2007
- 2007-03-23 KR KR1020070028621A patent/KR20070041697A/en active Search and Examination
Also Published As
| Publication number | Publication date |
|---|---|
| DK1582706T3 (en) | 2008-09-29 |
| EP1582706B1 (en) | 2008-07-16 |
| EP1582706A3 (en) | 2005-11-09 |
| CN1676888B (en) | 2010-09-01 |
| DE602005008126D1 (en) | 2008-08-28 |
| KR100750542B1 (en) | 2007-08-20 |
| CN101054913A (en) | 2007-10-17 |
| CN1676888A (en) | 2005-10-05 |
| KR20060045405A (en) | 2006-05-17 |
| EP1582706A2 (en) | 2005-10-05 |
| KR20070041697A (en) | 2007-04-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100549369C (en) | Cylinder lubricating system and to the method for cylinder supplying lubricating oil | |
| JP5519784B2 (en) | Method for lubricating a cylinder of a marine engine | |
| JP2011256867A (en) | Large engine with cylinder lubrication device and method for lubricating large engine cylinder | |
| CN105673125B (en) | Cylinder lubrication device and the method for operating the cylinder lubricating system | |
| CN101384815A (en) | Fuel injection system for internal combustion engine | |
| CN101749072A (en) | Detection device, method for operating stroke piston internal combustion engine, and stroke piston internal combustion engine | |
| EP2102487B1 (en) | Fuel pump and a method for controlling a fuel pump | |
| KR20020085808A (en) | A method of injecting lubricating oil in a cylinder of an internal combustion engine | |
| EP2196639A1 (en) | A cylinder oil dosage pump, a cylinder lubricating system, and an internal combustion engine | |
| KR20180122680A (en) | Methods and systems for introducing lubricating oil into cylinders, preferably two-stroke diesel engines, and the use of such methods and systems | |
| JP2006241989A (en) | Cylinder lubricating method and its device | |
| JP6177537B2 (en) | Method for lubricating a large engine including a cylinder lubrication device or a cylinder of a large engine | |
| WO2015129641A1 (en) | Cylinder lubrication system and cylinder lubrication method | |
| JP3897770B2 (en) | Internal combustion engine with cylinder lubrication device | |
| KR101765187B1 (en) | System for influencing the sliding properties of a sliding pair | |
| EP2484875B1 (en) | Cylinder lubrication device | |
| CN115443371B (en) | Method for lubricating large low-speed marine diesel engine | |
| KR20070108802A (en) | A method of causing a forced change in rotational position of piston rings, and a two-stroke internal combustion engine of the crosshead type |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20170911 Address after: Tokyo, Japan, Japan Co-patentee after: Japan motor Limited by Share Ltd Patentee after: Mit-subishi Heavy Industries Ltd. Address before: Tokyo, Japan, Japan Patentee before: Mit-subishi Heavy Industries Ltd. |
|
| TR01 | Transfer of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20091014 Termination date: 20210331 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |