CN103244302A - Large engine with cylinder lubrication device and method for lubricating cylinder thereof - Google Patents
Large engine with cylinder lubrication device and method for lubricating cylinder thereof Download PDFInfo
- Publication number
- CN103244302A CN103244302A CN2013100516400A CN201310051640A CN103244302A CN 103244302 A CN103244302 A CN 103244302A CN 2013100516400 A CN2013100516400 A CN 2013100516400A CN 201310051640 A CN201310051640 A CN 201310051640A CN 103244302 A CN103244302 A CN 103244302A
- Authority
- CN
- China
- Prior art keywords
- pressure
- connecting line
- piston
- big
- cylinder
- 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
Links
- 230000001050 lubricating effect Effects 0.000 title claims abstract description 52
- 238000005461 lubrication Methods 0.000 title claims abstract description 21
- 238000000034 method Methods 0.000 title claims abstract description 19
- 239000012530 fluid Substances 0.000 claims abstract description 11
- 238000001816 cooling Methods 0.000 claims abstract description 9
- 239000008041 oiling agent Substances 0.000 claims description 119
- 230000009467 reduction Effects 0.000 claims description 10
- 238000007789 sealing Methods 0.000 claims description 10
- 238000006073 displacement reaction Methods 0.000 claims description 4
- 238000002485 combustion reaction Methods 0.000 description 26
- 239000000659 freezing mixture Substances 0.000 description 23
- 239000000314 lubricant Substances 0.000 description 17
- 238000011156 evaluation Methods 0.000 description 12
- 230000000875 corresponding effect Effects 0.000 description 11
- 230000002000 scavenging effect Effects 0.000 description 11
- 239000000446 fuel Substances 0.000 description 10
- 238000012856 packing Methods 0.000 description 6
- 230000008859 change Effects 0.000 description 4
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 4
- NINIDFKCEFEMDL-UHFFFAOYSA-N Sulfur Chemical compound [S] NINIDFKCEFEMDL-UHFFFAOYSA-N 0.000 description 3
- 239000002253 acid Substances 0.000 description 3
- 210000003141 lower extremity Anatomy 0.000 description 3
- 239000000243 solution Substances 0.000 description 3
- 239000002826 coolant Substances 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000000994 depressogenic effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000006386 neutralization reaction Methods 0.000 description 2
- 230000003472 neutralizing effect Effects 0.000 description 2
- 229910052717 sulfur Inorganic materials 0.000 description 2
- 239000011593 sulfur Substances 0.000 description 2
- 239000002344 surface layer Substances 0.000 description 2
- 230000008016 vaporization Effects 0.000 description 2
- 238000009834 vaporization Methods 0.000 description 2
- 239000005864 Sulphur Substances 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000002596 correlated effect Effects 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 230000003628 erosive effect Effects 0.000 description 1
- 235000003642 hunger Nutrition 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000007689 inspection Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000001151 other effect Effects 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 239000013049 sediment Substances 0.000 description 1
- 230000008054 signal transmission Effects 0.000 description 1
- 230000037351 starvation Effects 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 238000007751 thermal spraying Methods 0.000 description 1
- 239000002912 waste gas Substances 0.000 description 1
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
- F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
- F01M11/10—Indicating devices; Other safety devices
-
- 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
- F01M1/18—Indicating or safety devices
- F01M1/20—Indicating or safety devices concerning lubricant pressure
-
- 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
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 provides a large engine with a cylinder lubrication device and a method for lubricating the cylinder thereof. The large engine has a cylinder sleeve, a drive shaft and a piston capable of being arranged in the cylinder sleeve movably, and a connecting element for connecting the drive shaft with the piston. The large engine also comprises a device for lubricating or cooling the cylinder and/ or the piston and/or the connecting element with the help of a fluid medium, and also comprises a first connecting pipe (11) used for transmitting the fluid medium from a reservoir to a work place. The first connecting pipe partly runs through the connecting element such that the fluid medium in the first connecting pipe is forced substantially under a pressure (P1). The large engine is equipped with a second connecting pipe (12) which receives a fluid medium that is forced under a pressure (P2), and under a normal operation mode, the pressure P2 is higher than the largest pressure P1.
Description
Technical field
The present invention relates to a kind of big-block engine that comprises the cylinder lubrication device, and relate to a kind of method on operation surface of cylinder wall of the cylinder for lubricated big-block engine.
Background technique
Big-block engine is internal-combustion reciprocating-pisto, and this internal-combustion engine especially is used for for example shipbuilding as the low cruise large-scale diesel engine.Big-block engine is usually as drive train peculiar to vessel or for example also be used for Fixed Point Operation to drive the high-rating generator for generation of electric energy.In this respect, with the continuous operation mode operation quite a long time, this effort and cost to handling safety and usability has high request to motor usually.For this reason, especially the economic expansion of Chang service intervals, low wearing and tearing and fuel and operative material, especially oiling agent to operate machines for the operator be central standard.Except other factors, the piston operation action of this big cylinder diameter low cruise big-block engine is for endurance of service intervals, usability and directly for the running cost that causes by oiling agent consumption and be determinant factor for business efficiency therefore.Therefore, the significance of the lubricated challenge of big-block engine constantly increases.
For big-block engine, but not only for these, lubricating fitting in the piston that piston lubrication is to move back and forth in the cylinder wall by layout takes place, by lubricating fitting lubricant oil is applied on the operation surface of cylinder wall, in order to make the minimise friction between piston and the operation surface and operation surface and wear of piston-rings are minimized.For example, for modern motor, for example
The RTA motor, the wearing and tearing on operation surface for duration of operation of 1000 hours less than 0.05mm.Be used for the about 1.0g/kWh of oiling agent delivery volume of such motor and littler, and at least for the cost reason should even further reduce, if possible, wearing and tearing and leak and must be minimized simultaneously.
Many different solutions are known as the lubrication system for lubricated operation surface, and this system is about the particular design of lubricating fitting itself, and also about lubricating method.For example, known such lubricating fitting, wherein lubricant oil is applied in operation by on the piston of these openings by a plurality of lubricant aperture, and these openings are arranged in the cylinder wall along peripheral direction, and wherein oiling agent is along peripheral direction and in axial direction distribute via piston ring.Oiling agent is not applied in according to this method on the large size on operation surface of cylinder wall, but more or less pointwise is applied to the side surface place of piston between the piston ring.
Known other method also in this respect.Therefore, for example, the lubrication system of advising among the WO00/28194, wherein, lubricant oil under high pressure is ejected into the scavenging air that is present in the combustion space with cylinder wall by the vaporization nozzles that is arranged in cylinder wall substantially tangently, and wherein lubricant oil is vaporized into particulate.Therefore, the lubricant oil of vaporization is distributed in the scavenging air and subtly owing to be thrown on the operation surface of cylinder wall by the centrifugal force of distortion generation, this operation surface support scavenging air, and therefore also support the lubricant oil particle that is distributed in subtly in the scavenging air.
In diverse ways, a plurality of oiling agent nozzles preferably are arranged in the mobile piston, wherein term can comprise simple discharge aperture and/or have the unit of safety check, makes oiling agent can be applied in place, the arbitrfary point on whole height on operation surface substantially.
How oiling agent is applied in the lip-deep type of operation and the mode of cylinder wall, and the time point that its dosage and oiling agent are introduced in the cylinder of big-block engine has material impact to lubricating quality.
The amount of moving lip-deep oiling agent that is applied to time per unit and per unit area depends on the many different parameters between the big-block engine on-stream period.Therefore, for example, the chemical composition of employed fuel, especially its sulphur content is being played the part of important role.Except cylinder is lubricated, this means between piston and the cylinder operation surface, more specifically the friction between the operation surface of piston ring and cylinder wall reduces, except other effect, oiling agent also is used for the erosion acid that produces, especially vitriolated neutralization during the combustion process of the combustion space of motor.For this reason, depend on employed fuel, use different types of oiling agent, except other difference, the difference of fuel is their neutralising capacity, and for this neutralising capacity, the so-called BN value of oiling agent is to estimate.Therefore, compare with the fuel with low sulfur content, advantageously use the oiling agent with higher BN value for the high sulfur content in the fuel, this is because the oiling agent with higher BN value has the higher neutralization about acid.
Yet usually also possible is that the oiling agent of same type must be used for the fuel of different quality.In this case, so, for example, the corresponding increase of the amount that higher or lower acid content can be by employed oiling agent or reduce and in combustion products, be compensated.
Present about another problem of the dosage of the amount of oiling agent to be applied state (the especially time deviation of the thickness of lubricating film and/or space bias under the running state of internal-combustion reciprocating-pisto) by lubricating film.
Naturally, the amount of required oiling agent can for example also depend on different Operational Limitss, such as revolution, combustion temperature, engine temperature, the available cooling performance of cooled engine, load and many other Operational Limitss.Therefore, possiblely be, for given revolution and higher load, compare with less load with same number of revolutions, the oiling agent of difference amount must be applied on the operation surface of cylinder.
In addition, the state of internal-combustion engine itself is also influential to the amount of oiling agent.Therefore, for example, be known that the amount of oiling agent to be used can be depending on the surperficial variations consumingly such as state of wear of cylinder operation of the piston ring of piston.Therefore, for the cylinder with new off-duty cylinder operation still surface and/or for the new piston ring that is in running in stage, really wish to increase to a certain extent friction, make opposite running counterpart (this means for example piston ring, piston ring groove, and operation is surperficial) but break-in, and can therefore relative to each other arrange ideally.Except other result, this can realize thus, compares with the cylinder that moves a large amount of hours runs, and the oiling agent with the difference amount comes work usually during the running in stage of cylinder.For this reason, for the motor with a plurality of cylinders, especially for each cylinder, the setting that usually can be separated from each other of the amount of oiling agent.
And cylinder operation surface usually will be along peripheral direction and differently wearing and tearing along the longitudinal direction, and irrelevant with the hours run of serving.For example this also is similarly definite for piston ring and piston itself.
Therefore, the amount of oiling agent not only must depend on the hours of operation of serving internal-combustion reciprocating-pisto and set, and the amount of oiling agent also should depend on according to the time and variable according to the application type of position dosage in the difference on the operation surface of cylinder wall is in one and same cylinder.
For this reason, early knownly provide the oiling agent nozzle in the operation surface of cylinder or in the zones of different in the mobile piston, these nozzles are preferably all controlled separately, make the amount of oiling agent can be depending on the application of time and position and change flexibly.
In order to determine to treat at particular point in time the amount of the oiling agent introduced by the particular lubricants nozzle, known many distinct methods.Under simple situation, may consider the amount of oiling agent of instruction of employed quality of fuel and oiling agent itself according to for example simply being controlled as the running state of the internal-combustion reciprocating-pisto of the function of load or revolution, the state of wear of the counterpart that wherein turns round on the contrary also can be considered based on the hours run of having served.
Therefore, those of ordinary skills can distinguish so-called hydrodynamic lubrication and not enough lubricating status and/or mixed lubricating state.People touch upon and have been formed between the opposite running counterpart at the such lubricating film of thickness, this means, the state of hydrodynamic lubrication in the time of for example between the piston ring of the operation surface of cylinder wall and piston, the surface of opposite running counterpart separates each other well by lubricating film, makes these can not contact with each other.Different border condition is shown by so-called mixed friction or mixed lubricating state.Under the situation of the state of mixed friction, the lubricating film that turns round on the contrary between the counterpart is so thin at least in part, makes opposite running counterpart directly contact with each other.In this case, there are danger and the last formation of embracing cylinder of scratch.So-called not enough lubricating status is treated to find between these two border condition.Under the state that deficiency is lubricated, lubricating film is accurately so thick to make opposite running counterpart no longer contact with each other; Yet the amount of oiling agent does not so enough make and form hydrodynamic lubrication between opposite running counterpart.Prevent previous mixed lubricating state and not enough lubricating status as much as possible.This means that the thickness of lubricating film preferably is selected such that to set the state of hydrodynamic lubrication between opposite running counterpart.
Operation causes correspondingly high oiling agent consumption naturally under the state of hydrodynamic lubrication.This is not only quite uneconomical on the one hand, and demonstrates surprisingly, and not only lubricant starvation, and excess lubricant can both cause the damage of opposite running counterpart in the cylinder.
This problem is successfully solved for the first time, this is because by sensor and determined the characteristic parameter of lubricating film under the running state by means of regulon evaluation sensor signal subsequently, the thickness of status parameter, the especially lubricating film of the lubricating film of cylinder operation surface preferably the corresponding dosage by the oiling agent supply by local optimum.Corresponding equipment and the method that is associated were at length discussed in EP1505270A1 by the claimant.
Solved ideally by the innovation method though determine the problem of the aequum of the oiling agent that must be supplied in a certain position on cylinder operation surface, still had difficulties up to now being identified for the ideal time that oiling agent injects cylinder put.
About this point, ideal time puts and can be depending on many parameters, especially depends on the different running statees of internal combustion engine operation.In the parameter that can play a role about this point some are identical, and they are correlated with for correct lubrication film thickness, and these parameters are listed in preface.Especially, correct time point depends primarily on above-mentioned different lubricating method naturally.Therefore the time point that is used for injecting oiling agent depends on lubricating method naturally strongly, and no matter oiling agent should for example be introduced in the scavenging air or for example should directly be injected the piston that running is passed through, and for example injects the piston-ring packing of piston.
Oiling agent pipeline for the piston that oiling agent is supplied to internal-combustion engine can especially extend in the inside of piston rod.Oiling agent also can be used for the bearing of lube pistons bar, and this is shown in the JP60-125713.This oiling agent is supplied to bearing from the cylinder internal space via reservoir or via supplying with rear line.Piston rod is directed in Stuffing box.The Stuffing box housing was maintained to be depressed, and this is because air is pumped in the Stuffing box by the reciprocating pump by piston operation.Because the Stuffing box housing was maintained at and depressed, therefore prevent that oiling agent from exposing, this means and avoided leakage.
Yet the Stuffing box shell space is fixed and it is possible with the plain mode sealing for this reason.Connect (jointed connection) for joint, for this purpose, must provide housing, this housing is implemented the motion of joint connection or encapsulates whole joint to connect, and this causes the very high requirement to forced air.For this reason, as if the solution that provides among the JP60-125713 is leaked impracticable for the oiling agent of avoiding relating to the joint connection.
Because with the problem that is associated via piston supply oiling agent; a plurality of solutions have been developed; these schemes are especially guaranteed lubricated between the inwall of piston and cylinder sleeve; this is because lubricated position is provided, and introduces oiling agent by injection or by nozzle at the cylinder jacket wall via these lubricated positions.
And, for the effectively lubricating of realizing the bucket cylinder unit, except the amount and its distribution of lubricant oil, be extremely important introducing the position of time point piston in cylinder.This position also has the so-called crankangle of the bent axle of motor to describe.Particularly, for very small amount of oiling agent, it is littler that the amount of oiling agent is that above-mentioned reason should become, and importantly, is in piston position place correct in the cylinder in the tram of piston and applies oiling agent.Only thereby guarantee effectively utilizing as far as possible of minor amounts of lubricants.
For the concept of the lubricating fitting that has the oiling agent nozzle in the mobile piston, oiling agent must be transported to the oiling agent nozzle via length, complicated supply, this long, complicated supply therefore with tolerance, use the frequency dependence connection of curved bar.Because of structure space reason and owing to the valve of the operating conditions in the cylinder for the rationing oiling agent only is arranged in outside the cylinder.Therefore, the supply line that is used for big-block engine has several Mi Changdu, and has very complicated structure between this external valve and the oiling agent nozzle.The control of valve can very accurately be carried out really; Yet the delay between the actual introducing of control and oiling agent can not reduce and can not accurately be scheduled to for this reason fully.And the amount that can not guarantee oiling agent controlled under valve in fact also arrives the oiling agent nozzle and is introduced at this long supply line scope built-in lubrication agent nozzle place.For this reason, time point and therefore the piston position in the cylinder can not accurately set to be used for the actual introducing of oiling agent cylinder sleeve, and the amounts of lubrication of introducing can not accurately be set.
Summary of the invention
For this reason, the object of the present invention is to provide a kind of improved lubricating fitting and a kind of operation surface of improved cylinder for lubricated big-block engine is provided and detects the method that the oiling agent of oiling agent supply system leaks.The cooling system that another object of the present invention is to provide a kind of joint of improved piston rod for cross head engine to connect especially provides a kind of device for the leakage of avoiding cooling system.
Big-block engine according to the present invention comprises cylinder sleeve, can be arranged in piston, the live axle in this cylinder sleeve and the connecting element that is used for this live axle is connected to described piston with being shifted.Described big-block engine also comprises for lubricated by flowing medium or cool off the device of described cylinder and/or described piston and/or described connecting element, and comprises for first connecting line that described flowing medium is transported to the place to use from reservoir.Described first connecting line extends through described connecting element at least in part, and wherein, the described flowing medium in described first connecting line is pressurized pressure P 1 time basically.Also be provided with second connecting line, this second connecting line receives flowing medium, and this flowing medium is pressurized pressure P 2 times, and under normal manipulation mode, pressure P 2 is higher than pressure maximum P1.
Particularly, because the reducing and can survey of the pressure P 1 that causes of leakage in described first connecting line, the leakage in described first connecting line causes the decompression in described first connecting line, and therefore causes the pressure reduction between P1 and the P2 to increase.Therefore leakage in described second connecting line causes reducing of pressure P 2, and reducing of pressure reduction between P1 and the P2 taken place.
Described connecting element comprises the piston rod with crosshead, wherein, described crosshead comprises joint, in this joint adjacency at least one connecting rod is arranged, described at least one connecting rod is connected to described live axle, makes that rotatablely moving of described live axle can be by the displacement of described piston and produce.
According to mode of execution, in described joint, can be provided with a plurality of holes.These holes can be the parts of described second connecting line.Can between described joint and the described reservoir for generation of pressure P 2, pump be set.Alternatively, described reservoir itself can maintain pressure P 2 times, even maintains under the higher pressure, in order to compensate the pressure loss in the described pipeline.Under normal manipulation mode, pressure P 2 is constant basically.Described pump can be connected to described first connecting line via throttle element.Particularly, can be provided with pulse oscillator between described throttle element and described first connecting line, wherein, described pulse oscillator comprises at least one valve or guiding valve or solenoid valve particularly.The joint arm can be set, be used for described flowing medium is supplied to described first connecting line and/or described second connecting line.This joint arm is called as curved bar.Alternatively, for example, also pressure hose can be set.
In described first connecting line and described second connecting line, can be provided for detecting the pressure transducer of leakage, in order to detect pressure P 1 in described first connecting line and the pressure P 2 in second connecting line.Described pressure transducer sends the signal that can be introduced into evaluation unit.Measured pressure can with described evaluation unit in corresponding reference pressure compare.If produce the pressure reduction of the fluctuation width that surpasses operation pressure, the then alarm of output indication leakage.
The place to use that is used for according to device of the present invention can for example be cylinder lubrication, comprises for the lip-deep lubricating point of operation that oiling agent is applied to described cylinder.Naturally, also a plurality of lubricating points can be set in the same manner.Particularly, can between described second connecting line and crankshaft space, Sealing be set.
The invention still further relates to a kind of method for lubricated or cooling large-sized motor, wherein, described big-block engine comprises cylinder sleeve, can be arranged in piston, the live axle in this cylinder sleeve with being shifted and be used for this live axle is connected to the connecting element of described piston, and comprises for lubricated by flowing medium or cool off the device of described cylinder and/or described connecting element.Described flowing medium is transported to the place to use from reservoir.Be provided with first connecting line, this first connecting line extends through described connecting element at least in part.Described flowing medium is pressurized pressure P 1 time basically in described first connecting line.Be provided with second connecting line, this second connecting line receives flowing medium, and this flowing medium is pressurized pressure P 2 times, and under normal manipulation mode, pressure P 2 is higher than pressure maximum P1.Pressure P 1 can be particularly owing to the leakage in described first connecting line reduces.
Described reservoir can be designed for the common-rail reservoir of oiling agent or freezing mixture, and this reservoir is connected to all oiling agent pipeline or the coolant lines for corresponding cylinder.Therefore, can guarantee to have identical pressure in each oiling agent pipeline or each coolant lines.
Lubricating point can be about by the definite diverse location place that is disposed axially in cylinder wall of the longitudinal axis (A) of cylinder.When oiling agent not only is introduced at a plurality of somes place around the cylinder circle distribution, but also when different axial positions were introduced into, oiling agent can evenly distribute in the big surface range on operation surface.Applying thus of oiling agent can take place simultaneously, this means, all locking members are opened at identical time point.Yet, can also introduce oiling agent in different time points, this means for example to lubricate and move prior to piston.
Further application of the invention is to detect the leakage for the freezing mixture of the cylinder of big-block engine or piston.Freezing mixture can be in cylinder wall or the flowing medium that circulates in the inside of piston.Freezing mixture can be transported to corresponding place to use by pump as oiling agent.
Pump can be specifically designed to have the reciprocating pump of a plurality of feeding pistons.Described feeding piston is preferably by camshaft actuated.Described camshaft can be particularly by motoring.For this reason, the revolution of described camshaft (this means the intake stroke number of time per unit) can change arbitrarily in by the scope of the predetermined revolution of described motor.According to another modification, described feeding piston also can be connected to working piston, and wherein, described working piston can move by fluid pressure device, makes to produce the feeding hub.Described feeding piston conveyor lubricant or freezing mixture in distributor.When the described feeding piston of rotary piston pump was implemented their intake stroke one by one, particularly, when the cam arrangement of described camshaft became to be shifted angularly each other, the pressure divergence in the described distributor can be reduced.
Fluid pressure device can be oiling agent or the freezing mixture that is provided by additional reservoir.This reservoir is in particularly than being used under the high pressure of lubricated reservoir.This reservoir can be in and surpass under the pressure of 50 bar, typically, is reaching from 50 bar and is comprising in the pressure range of 100 bar.The oiling agent that is used for lubricating fitting is provided by the reservoir that is under the pressure that reaches 50 bar particularly.The pressure of oiling agent or freezing mixture reaches 50 bar for pulse, and preferably is in the scope of from 40 to 50 bar under the pressure of foundation in the scope of from 10 to 15 bar.This pressure wherein must be considered the pressure loss in the pipeline corresponding to pressure P 1.The use that is in two reservoirs (this often means that lubricant reservoir or lubricant container or freezing mixture reservoir) under the pressure reduction allows with oiling agent or freezing mixture operating pumps.Thus, between driving fluid and operating fluid (this means for lubricated oiling agent or freezing mixture), Sealing is set and becomes out-of-date.Can economize thus except seal element is set in pump, this causes more cost to make pump effectively, and causes operation and maintenance to be simplified.
Be used for the pressure of reservoir of lubricating fitting preferably less than the pressure of the reservoir of the actuating of the working piston that is used for pump.
The setting of locking member is preferably carried out according to the load of big-block engine.Therefore, needs can be accurately mated in the oiling agent supply.
The setting of locking member is particularly according to the position of the cylinder of crankangle and/or revolution and/or moment of torsion and/or big-block engine and carry out.
According to concrete and simple modification when the pressure in the cylinder space is higher than the feed pressure of oiling agent, stops to supply oiling agent on the operation surface of cylinder wall.Therefore, can guarantee when piston is near upper dead center, not have oiling agent to arrive the combustion space of cylinder.Therefore can prevent that oiling agent is present in the combustion space during combustion process, and therefore prevent from causing the burning of oiling agent, otherwise this burning may cause undesirable sediments and waste gas.
Evaluation unit be measured and be transferred to the pressure of oiling agent for example can by pressure transducer.This evaluation unit checks whether pressure is in the predetermined pressure range that is limited by upper threshold value and lower threshold value.Carry out this inspection at pressure P 1 and pressure P 2 boths.Evaluation unit calculates the pressure reduction between P2 and the P1.Under normal manipulation mode, pressure P 2 is in more than the pressure of P1.If pressure reduction is born, the then existence of this indication leakage.
For Negative Pressure Difference, can give the alarm.Drop under this pressure, especially drop to the leakage that can indicate under this pressure in the lubricating fitting in longer a period of time, this lubricating fitting must be checked immediately so that the damage of avoiding causing because of lack of lubrication.
Description of drawings
With reference to schematic representation the present invention is described in further detail hereinafter.Show:
Fig. 1 is the section that runs through the bucket cylinder device in the big-block engine;
Fig. 2 is for the cylinder according to the two-stroke large diesel engine of a mode of execution according to lubricating fitting of the present invention;
Fig. 3 is the details for the assembly of determining the pressure reduction between first connecting line and second connecting line;
Fig. 4 is the schematic representation of oiling agent supply;
Fig. 5 is for the process of the lubrication pressure P1 under the normal manipulation mode and P2 and the p, the t plotted curve that are used for fault.
Embodiment
Schematically show the section that runs through big-block engine among Fig. 1.Big-block engine according to Fig. 1 has cylinder unit, and this cylinder unit has cylinder and the piston 25 that is cylinder sleeve 20 forms.Cylinder unit also has fresh air supply system 101.The cylinder unit of Fig. 1 is the typical device for longitudinally scavenged two-stroke large diesel engine well known in the prior art.
Piston 25 is arranged to and can back and forth be shifted by the cylinder wall 22 along cylinder sleeve 20 in cylinder sleeve 20.Piston 25 moves back and forth between two turning points (that is, upper dead center (OT) and lower dead centre (UT)), and wherein upper dead center (OT) is arranged between lower dead centre (UT) and the outlet valve 102.
Piston 25 comprises piston-ring packing, this piston-ring packing is shown schematically as in Fig. 2 only has three piston rings 27,28,29, namely, the most close outlet valve 102 and therefore also be also referred to as apical ring near the upper piston ring 28(of combustion space 23), in Fig. 2, be arranged in second piston ring 27 under the first piston ring 28 with respect to outlet valve 102, and be arranged in another piston ring 29 under the piston ring 27.
According to diagram, combustion space 23 at the top by the cylinder head 103 with nozzle and outlet valve 102 limited boundaries, described nozzle is not shown in detail, and fuel can be injected combustion space 23 by means of this nozzle, and described outlet valve 102 is shown as in the closed position in Fig. 1.
Piston 25 is connected to crosshead 14 via piston rod 13 in a manner known way, and at the big-block engine run duration, the to-and-fro motion of piston 25 is delivered to the bent axle of big-block engine from piston rod 13.According to diagram, piston rod 13 is guided through gas-swept space 110 and passes Stuffing box 111, described gas-swept space 110 for outlet valve 102 in abutting connection with the bottom of cylinder sleeve 20, described Stuffing box 111 comes gas-swept space 110 and crankshaft space 115 sealings that are positioned under it, makes can not arrived the crankshaft spaces 115 from gas-swept space 110 by arrow 112 represented fresh airs.Turbosupercharger 113 under high pressure (for example, under the pressure up to 4 bar) is transported to gas-swept space 110 with fresh air.
Piston 25 is designed to use freezing mixture 70 at inner colded piston 25, and wherein, freezing mixture is supplied and removed via unshowned supply line.
Piston 25 is shown as in Fig. 1 in the position that is between OT and the UT.Along the direction of outlet valve 102, piston top edge 71 is limited by the point of going up most on the cover surface 72 of piston 25.Piston 25 is arranged to can be along piston axis back and forth displacement vertically on the direction of lower dead centre in cylinder sleeve 20.
Piston 25 is designed to two-piece type.It comprises so-called piston top 73 and is screwed in piston skirt 74 on the piston top 73 by unshowned screw thread that wherein, piston top 73 is arranged along the direction of outlet valve, and piston skirt 74 is arranged along the direction of gas-swept space 110.Piston skirt 74 has the cover surface of tubular, and the minimum point on this cover surface limits along the piston skirt lower limb 75 of the direction of gas-swept space 110.
Three piston rings 27,28,29 shown in Figure 2 are arranged in 72 places, cover surface on piston top 73, the first, upper piston ring 28 is arranged along the direction of outlet valve, the second adjacent piston ring 29 arranges along the direction of piston skirt lower limb 75, and three piston ring 27 adjacent with second piston ring 29 arranged along the direction of piston lower limb 25.Piston ring 27 is positioned between upper piston ring 28 and the lower piston ring 29.
According to Fig. 2, oiling agent and freezing mixture pass piston rod 13 and are transferred to piston 25.According to Fig. 1, oiling agent and/or freezing mixture are supplied to piston rod 13 via crosshead 14.For this purpose, crosshead is included in the passage that is shown specifically among Fig. 3.These passages are via curved bar 120 supplies.Reservoir 30(fixing on the curved bar 120 expression positions is referring to Fig. 2) and crosshead 14 between connecting element, can between reservoir 30 and crosshead 14, pump 1 be set.Alternatively, reservoir 30 can be designed to be similar to the common-rail reservoir, and can comprise oiling agent or freezing mixture pressurized under enough high pressure.Therefore enough high pressure should be understood to be in the above pressure of pressure P 1 and/or P2, and the pressure loss that is enough to the supply of balance crosshead 14.
As shown in Figure 1, curved bar 120 itself can have one or more joint link so that the motion of balance crosshead.
Cylinder mode with sectional drawing in Fig. 2 of two-stroke large diesel engine with lubricating fitting 10 is schematically illustrated.The two-stroke large diesel engine of Fig. 2 comprises a plurality of cylinders 20, wherein, for clear, only exemplarily shows a cylinder 20.Cylinder 20 comprises cylinder wall 22, and this cylinder wall limits the inner space 23 of cylinder 20 in a manner known way along peripheral direction.Piston 25 is arranged in the cylinder 20, and this piston is arranged to and can back and forth be shifted with respect to the axial direction A of the cylinder 20 operation surface 21 along cylinder wall 22.Operation surface 21 can be arranged on the surface layer place, and this surface layer for example is applied in by means of thermal spraying on the surface of cylinder wall 22.At least one lubricating point 7,17(be lubricating nozzle 26,46 especially) be arranged in the cylinder wall 22, this cylinder wall is supplied oiling agent in a manner known way by pump 1, makes lubricating film can be applied under running state on the operation surface 21 on the cylinder wall 22.
Lubricating point 7,17 is connected to pump 1 via lubricated pipeline 8,18.In the lubricated pipeline each all has locking member 5,15.Lubricated pipeline is the part of distributor 3, and this distributor also can be designed to the common-rail reservoir.Pump 1 is transported to lubricating point 7,17 from reservoir 30 by distributor 3 with oiling agent.This layout can use freezing mixture to replace oiling agent in order to use when cooling piston or cylinder.
The oiling agent that is introduced in the working piston space 34 of pump 1 arrives feeding spaces 36 via corresponding opening 39.As long as working piston is present in the working piston space 35, opening 39 just is connected to working piston space 34, this means, the stroke of pump 1 does not start as yet.Oiling agent one is applied on the working piston in the working piston space 34, and this just sets the motion of the resistance of opposing holding device 37 for.Each opening 39 is by 38 sealings of feeding piston, and the oiling agent that is present in the feeding space 36 is compressed.Because feeding space 36 is connected to distributor 3 in the mode of fluid conduction, therefore the oiling agent that is present in distributor 3 and/or the oiling agent pipeline 8,18 is also compressed.
When intake stroke was finished, oiling agent had obtained required pressure in oiling agent pipeline 8,18.This pressure can be by means of the pressure monitor sensor in the distributor 3, and no matter pressure whether be present in guarantee lubricated required can predetermined bandwidth in.This bandwidth is in the scope of from 10 to 50 bar usually, and particularly, this scope comprises that the pressure of foundation of from 10 to 15 bar is to the pressure that is used for pulse that is in 40 to 50 bar.
Therefore oiling agent is provided in the oiling agent pipeline 8,18, in order to be applied in 21 places, operation surface of cylinder 20 at desirable time point.Desirable time point determined by central location 50, and this central location is sent to corresponding locking device 5,15 opening with signal via signal transmission line 42,43.Therefore, Run Hua time point can fully freely be determined by central location.
Naturally, locking device 5, shut-in time of 15 point can be determined arbitrarily by central location 50 equally.Therefore, required amounts of lubrication can be specific lubrication interval and accurately setting.
Exemplarily show measuring device 40 among Fig. 2, by this measuring device 40, detect the nominal value of the running state that is used for two-stroke large diesel engine.Measuring device 40 produces the electrical signal as the feature of nominal value, and this signal is transferred to central location 50 along signal transmssion line 41, and this central location 50 is used for the control lubrication system.In this central location 50, estimate aforementioned signal.If evaluation result requires to be lubricated, then signal is transferred to locking member 5,15 from central location via signal transmssion line 42,43, make these elements activated, this means that they are opened or closed for the through-flow of oiling agent.Signal also can be used for control pump 1.This can be used for feed current can reformed pump, for example, and the rotary pump such as recycle pump, wing pump.For example, the revolution of the motor of driven pump can be changed, and makes it possible to change the volume flow that time per unit is carried by pump.For rotary piston pump, also there is this possibility.This rotary piston pump generally includes a plurality of pistons, and these pistons are by means of being moved by electric motor driven camshaft.In order to increase the revolution of camshaft, increase the stroke of piston number of time per unit, and therefore change the volume flow of carrying by pump.Naturally, also can use the pump with single feeding piston, wherein, but feeding piston hydraulic pressure moves or can move by means of camshaft.
Under this situation, the switching frequency of switch valve 32 can be changed.In this case, signal is transferred to switch valve 32 from central location 50 via signal transmssion line 44.Particularly, switch valve is designed to solenoid valve.Switch valve 32 can be taked two positions.In the primary importance, the connection between working piston 33 and the reservoir 30 is opened, and makes oiling agent to be got back to the reservoir 30 from working piston space 34 supplies that working piston 33 is present in wherein.Connecting line between reservoir 30 and the feeding space 36 is opened, and makes oiling agent can flow in the feeding space 36.
Be spring in this example by holding device 37() take working piston 33 to its upper end position, and this working piston is prepared intake stroke now.When switch valve 32 obtained to carry out the signal of intake stroke from central location 50, its diverter switch made the connection that passes to reservoir 31 be opened.Under high pressure oiling agent is introduced the working piston spaces 35 from reservoir 31, and working piston 33 carries out intake stroke, this means, by feeding piston 38 oiling agent is pumped into the distributor 3 from the feeding space.In addition, working piston needn't separate with the feeding space with sealing means.Therefore, do not need to make driving side working piston space 35 and 34 sealings of feeding piston side working piston space to come.
Locking member 5,15 is opened the certain hour section, makes oiling agent be applied on the operation surface 21 based on the measured value of measuring device 40.The time period that each locking member 5,15 stays open can mate separately, and depends on the measured value that detects by measuring device 40.
Naturally, can provide a plurality of measuring devices, these measuring devices are measured the different parameters of big-block engine.
Can set the pressure of oiling agent equally, make it be between the pressure maximum and the pressure minimum in the combustion space in the combustion space.Pressure in the combustion space is in more than the lubricant pressure when the time point of the final stage of compression stroke, fuel air mixture igniting and expansion stage begin at least, and making does not have oiling agent to enter in the combustion space.Only when the pressure in the combustion space during the expansion stage, during the fresh air supply or be in the pressure of oiling agent during the phase I of compression stroke when following, just oiling agent may be incorporated on the operation surface of cylinder.The alternative of this situation is, when piston had passed through lubricating point in compression stroke, the introducing of oiling agent was possible, this means, lubricating point leads to the cylinder space that is filled with scavenging air, and this scavenging air is pressurized under corresponding scavenging air pressure.Scavenging air pressure more or less is in usually more than the external pressure of about 3 bar in this usually.Therefore, between the position of lubricating point and piston, exist and connect.If piston (this means piston-ring packing) is positioned at the lubricating point top, then scavenging air pressure is present in the locking member place basically, and the pressure that is present in the combustion space (this means the cylinder space between piston-ring packing and the outlet valve) is significantly higher.
When lubricating point is in the zone that is covered by piston-ring packing during compression stroke thus, during the force feed oiling agent in the opposing cylinder space, in the time of near piston is present in upper dead center, oiling agent may arrive cylinder space, and this is basically less than the pressure in the combustion space side pressure in the cylinder space because of the pressure on the scavenging air side.
Also illustrate among Fig. 2, oiling agent or freezing mixture are supplied to piston 25.Device 10 according to the present invention is used for lubricating or cooling cylinder cover 20 and/or piston 25 and/or connecting element 13,14,19,120 by flowing medium.Flowing medium is freezing mixture or oiling agent specifically.First connecting line is arranged for flowing medium is fed to place to use 20,25,13,14,19 from reservoir 30.First connecting line 11 extends through connecting element 13,14,19 at least in part.The route that passes piston rod 13 only is shown among Fig. 1.Yet connecting line can be arranged in crosshead, curved bar and the piston in the same manner, especially is arranged in the piston skirt.Flowing medium is present in first connecting line for 1 time in pressure P basically.Be provided with second connecting line 12, in this second connecting line 12, receive the flowing medium under the P2 pressure.Pressure P 2 is higher than pressure maximum P1 under normal manipulation mode.
Fig. 3 shows the details of the device that is used for cooling between first connecting line 11 and second connecting line 12 and/or lubricates.Show the sectional drawing of the part of crosshead 14 and piston rod 13.According to Fig. 3, casing component 117 also is present between piston rod 13 and the crosshead 14.Because piston rod 13 can rotate with respect to crosshead, therefore be provided with Sealing 118, so that about crankshaft space 115 sealing first connecting line 11 and second connecting lines 12.
Flowing medium is present in first connecting line 11, and this flowing medium for example is freezing mixture or oiling agent.The flowing medium that is present in first connecting line has pressure P 1.First connecting line extends through piston rod 13, casing component 117, and passes crosshead 114.For this purpose, have open channels at the sleeve surface place of crosshead, this open channels is illustrated in connecting line 11 places and is connected to the supply line that extends through curved bar 120.Supply line and supply line to the connection of crosshead does not illustrate in the drawings.
Flowing medium circulates in second connecting line 12, and this flowing medium is pressurized pressure P 2 times in a similar manner.Particularly, for normal manipulation mode, pressure P 2 can be constant.Because therefore the pressure P 2 of the flowing medium in second connecting line, has guaranteed at first that the flowing medium of first connecting line can not be discharged to the outside greater than the pressure P 1 of the flowing medium in first connecting line.Under the situation that in first connecting line 11, takes place to leak, prevented that by means of the elevated pressures P2 in second connecting line flowing medium from exposing.For this reason, under the situation that takes place to leak in first connecting line 11, flowing medium can flow in first connecting line 11 with pressure P 2.Therefore, the pressure in first connecting line increases, and the pressure in second connecting line descends simultaneously, thereby pressure balance has taken place.Measured by the pressure decline that pressure balance causes, and be transferred to evaluation unit.Pressure and reference pressure that evaluation unit is constantly relatively surveyed.Pressure reduction is owing to pressure balance descends, and for this reason, evaluation unit sends signal, for example, and alarm.This alarm provides and has the signal that leaks in first connecting line.
When having leakage in second connecting line 12, pressure P 2 descends.Pressure P 2 is measured by evaluation unit about the decline of reference pressure.Evaluation unit also produces output signal in this case, for example, and alarm.This alarm can be different from the alarm that provides the signal that existence is leaked in first connecting line.
Fig. 4 shows a mode of execution, the figure shows the different pressures P1 and the P2 that produce by different way in first connecting line 11 and second connecting line 12.The flowing medium of carrying from reservoir 30 by pump 1 is divided into first connecting line 11 and second connecting line 12 by means of the components distributor that is not shown specifically.Pressure in the pressure line in pump downstream is corresponding with higher pressure P2 thus.In connecting line 11, be provided with throttle element 125, be used for reducing pressure.Also impulse sender 126 can be set in the connection at throttle element 125 places.Impulse sender is used for the dispense-pulse electric current.Particularly, when flowing medium is oiling agent, can advantageously export oiling agent sometime.Impulse sender can for example be designed to locking member, particularly, is designed to valve.
Plotted curve shown in Fig. 5 shows the route of the pressure of flowing medium, and this pressure representative is on the y axle, and time representation is on the x axle.Therefore, solid line shows urgent leak pressure P afterwards 2 and its variation takes place in second or first connecting line.In addition, pressure P 1 and its variation under the dotted line situation of representing in first connecting line 11 to take place to leak.As above illustrated, pressure P 1 increases when occurring leaking, and makes occurring pressure reduction as the pressure P 1 of reference pressure storage with owing to leak between the increased pressure P1 '.
In addition, plotted curve shows the pressure route of pulse when flowing medium is treated to carry with pulse mode.Under the normal manipulation mode of device, the pressure maximum of pulse is in below the minimum value of pressure P 1.
Naturally, according to device of the present invention, and be not limited to the embodiment shown in the accompanying drawing for detection of the method for leaking, but can produce at each fluid feed system according to the present invention.
Claims (15)
1. big-block engine, this big-block engine comprises cylinder sleeve (20), can be arranged in to displacement the piston (25) in this cylinder sleeve (20), live axle, and the connecting element (13 that is used for this live axle is connected to described piston (25), 14,19,120), described big-block engine comprises for the device that lubricates or cool off described cylinder and/or described piston and/or described connecting element by means of flowing medium, and comprise for described flowing medium is delivered to place to use (7 from reservoir (30), 17) first connecting line (11), described big-block engine is characterised in that, described first connecting line (11) extends through described connecting element at least in part, wherein, described flowing medium in described first connecting line (11) is pressurized pressure P 1 time basically, wherein, also be provided with second connecting line (12), this second connecting line is received in 2 times pressurized flowing mediums of pressure P, and under normal manipulation mode, described pressure P 2 is higher than maximum described pressure P 1.
2. big-block engine according to claim 1, wherein since the described pressure P 1 that the leakage in described first connecting line (11) causes reduce to be to survey.
3. big-block engine according to claim 1 and 2, wherein, because the reduction of the described pressure P 2 that the leakage in described second connecting line (12) causes is to survey.
4. according to each the described big-block engine in the aforementioned claim, wherein, described connecting element comprises the have crosshead piston rod (13) of (14), described crosshead has joint and in this joint adjacency at least one connecting rod (19) is arranged, described at least one connecting rod is connected to live axle, makes rotatablely moving of described live axle to produce by the displacement of described piston.
5. big-block engine according to claim 4 wherein, is provided with a plurality of holes in described joint, and described a plurality of holes are designed to the part of described second connecting line.
6. according to claim 4 or 5 described big-block engines, wherein, between described joint and described reservoir (30), be provided with pump (1), for generation of described pressure P 2.
7. according to each the described big-block engine in the aforementioned claim, wherein, described pressure P 2 is constant.
8. according to each the described big-block engine in the aforementioned claim, wherein, described pump (1) is connected to described first connecting line via throttle element (125).
9. according to each the described big-block engine in the aforementioned claim, wherein, be provided with pulse oscillator (126) between described throttle element (125) and described first connecting line (11), described pulse oscillator comprises at least one valve or guiding valve or magnet valve particularly.
10. according to each the described big-block engine in the aforementioned claim, wherein, be provided with joint arm (120), be used for described supplying fluid medium to described first connecting line (11) and/or described second connecting line (12).
11. according to each the described big-block engine in the aforementioned claim, wherein, in described first connecting line (11) and described second connecting line (12), be provided with corresponding pressure transducer, in order to detect described pressure P 1 in described first connecting line (11) and the described pressure P 2 in described second connecting line (12).
12. according to each the described big-block engine in the aforementioned claim, wherein, described place to use comprises cylinder lubrication, and comprises the lubricating point for the operation surface (21) that oiling agent is applied to described cylinder sleeve (20).
13. according to each the described big-block engine in the aforementioned claim, wherein, between described second connecting line (12) and crankshaft space (115), be provided with Sealing (118).
14. method that is used for lubricated or cooling large-sized motor, wherein, described big-block engine comprises cylinder sleeve (20), can be arranged in piston (25), live axle in this cylinder sleeve (20) with being shifted, and the connecting element (13,14,19,120) that is used for this live axle is connected to described piston, described big-block engine comprises that also wherein: described flowing medium is delivered to place to use (7,17) from reservoir (30) in connecting line for the device that lubricates or cool off described cylinder and/or described connecting element by means of flowing medium; Be provided with first connecting line (11), this first connecting line extends through described connecting element at least in part; Described flowing medium in described first connecting line (11) is pressurized pressure P 1 time basically; Be provided with second connecting line (12), this second connecting line is received in 2 times pressurized flowing mediums of pressure P, and under normal manipulation mode, described pressure P 2 is higher than maximum described pressure P 1.
15. method according to claim 14, wherein, described pressure P 1 is owing to the leakage in described first connecting line (11) descends, and/or, described pressure P 2 is owing to the leakage in described second connecting line (12) reduces.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP12155055.2 | 2012-02-13 | ||
| EP12155055 | 2012-02-13 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103244302A true CN103244302A (en) | 2013-08-14 |
| CN103244302B CN103244302B (en) | 2017-10-27 |
Family
ID=47504778
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310051640.0A Expired - Fee Related CN103244302B (en) | 2012-02-13 | 2013-02-08 | Big-block engine including cylinder lubrication device and the method for lubricating its cylinder |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2626525A1 (en) |
| JP (1) | JP6177537B2 (en) |
| KR (1) | KR20130093037A (en) |
| CN (1) | CN103244302B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107208625A (en) * | 2014-12-22 | 2017-09-26 | S.P.M.流量控制股份有限公司 | reciprocating pump with double loop power end lubricating system |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB201409064D0 (en) * | 2014-05-21 | 2014-07-02 | Castrol Ltd | Method and apparatus |
| CN110360074A (en) | 2014-07-25 | 2019-10-22 | S.P.M.流量控制股份有限公司 | Curved shaft support device |
| USD759728S1 (en) | 2015-07-24 | 2016-06-21 | S.P.M. Flow Control, Inc. | Power end frame segment |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09264116A (en) * | 1996-03-29 | 1997-10-07 | Nissan Diesel Motor Co Ltd | Oil pressure alarm device for marine engine |
| EP0903473A1 (en) * | 1997-09-22 | 1999-03-24 | Wärtsilä NSD Schweiz AG | Diesel engine and operating method therefor |
| JP2000204918A (en) * | 1999-01-18 | 2000-07-25 | Isuzu Motors Ltd | Lubricating mechanism in camshaft bearing part of engine |
| EP1640571A1 (en) * | 2004-09-28 | 2006-03-29 | Aisin Seiki Kabushiki Kaisha | Oily supply device for engine |
| US20070084431A1 (en) * | 2005-10-17 | 2007-04-19 | Omachi Steven T | Fluid pump and method |
| CN102278163A (en) * | 2010-06-11 | 2011-12-14 | 瓦锡兰瑞士公司 | Large engine with a cylinder lubrication device and method for lubricating a cylinder of a large engine |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2539522C2 (en) * | 1975-09-05 | 1982-12-02 | M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8900 Augsburg | Device for supplying lubricating oil to several lubrication points in an internal combustion engine, in particular a large engine |
| FR2909410A1 (en) * | 2006-12-05 | 2008-06-06 | Renault Sas | Oil supply system for internal combustion engine, has two pumps for supplying oil to lubrication system and nozzles, respectively, where lubrication system includes supplementary by-pass circuit connecting one pump to nozzles |
-
2013
- 2013-01-16 EP EP13151405.1A patent/EP2626525A1/en not_active Withdrawn
- 2013-02-08 CN CN201310051640.0A patent/CN103244302B/en not_active Expired - Fee Related
- 2013-02-12 KR KR1020130015023A patent/KR20130093037A/en not_active Application Discontinuation
- 2013-02-12 JP JP2013024191A patent/JP6177537B2/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09264116A (en) * | 1996-03-29 | 1997-10-07 | Nissan Diesel Motor Co Ltd | Oil pressure alarm device for marine engine |
| EP0903473A1 (en) * | 1997-09-22 | 1999-03-24 | Wärtsilä NSD Schweiz AG | Diesel engine and operating method therefor |
| JP2000204918A (en) * | 1999-01-18 | 2000-07-25 | Isuzu Motors Ltd | Lubricating mechanism in camshaft bearing part of engine |
| EP1640571A1 (en) * | 2004-09-28 | 2006-03-29 | Aisin Seiki Kabushiki Kaisha | Oily supply device for engine |
| US20070084431A1 (en) * | 2005-10-17 | 2007-04-19 | Omachi Steven T | Fluid pump and method |
| CN102278163A (en) * | 2010-06-11 | 2011-12-14 | 瓦锡兰瑞士公司 | Large engine with a cylinder lubrication device and method for lubricating a cylinder of a large engine |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107208625A (en) * | 2014-12-22 | 2017-09-26 | S.P.M.流量控制股份有限公司 | reciprocating pump with double loop power end lubricating system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2013164072A (en) | 2013-08-22 |
| KR20130093037A (en) | 2013-08-21 |
| EP2626525A1 (en) | 2013-08-14 |
| JP6177537B2 (en) | 2017-08-09 |
| CN103244302B (en) | 2017-10-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101415936B (en) | Crosshead type large-sized uniflow type two-stroke diesel motor | |
| JP5519784B2 (en) | Method for lubricating a cylinder of a marine engine | |
| JP5196981B2 (en) | Piston for oil collecting ring | |
| CN102278163A (en) | Large engine with a cylinder lubrication device and method for lubricating a cylinder of a large engine | |
| JP2008202550A (en) | Large-sized two stroke dual fuel diesel engine | |
| CN103244302A (en) | Large engine with cylinder lubrication device and method for lubricating cylinder thereof | |
| KR20190122261A (en) | Fuel injection system | |
| CN105569876B (en) | Cylinder, reciprocating piston internal combustion engine and method of operating the same | |
| KR20160051661A (en) | Gas supply system and cylinder for a reciprocating piston internal combustion engine, reciprocating piston internal combustion engine and method of operating a reciprocating piston internal combustion engine | |
| KR102110588B1 (en) | A cylinder liner for a two-stroke crosshead engine | |
| KR20070057960A (en) | Method and system for modifying a used hydrocarbon fluid to create a cylinder oil | |
| KR102632285B1 (en) | A lubrication device for a large diesel engine, a method for cylinder lubrication of a large diesel engine and a large diesel engine | |
| CN102449276B (en) | A lubrication oil pump, a cylinder lubricating system, and an internal combustion engine | |
| KR20130136942A (en) | Lubricant collection apparatus | |
| EP3483403B1 (en) | Lubrication arrangement for a large diesel engine | |
| US5769058A (en) | Compressor and engine system | |
| DK201500647A1 (en) | Method and apparatus for preparing an oil to be supplied to the cylinders of a two-stroke crosshead engine | |
| KR20130088076A (en) | Piston-in-cylinder unit and method of lubricant supply of a piston of a piston-in-cylinder unit for a reciprocating piston combustion engine | |
| JP2013238231A (en) | Method for lubricating cylinder inside piston device of reciprocating piston type combustion engine and cylinder lubricating device | |
| CN103527282A (en) | Lubrication system, lubricant injection device, and method for lubricating an internal combustion engine | |
| KR102299067B1 (en) | Multi-lubricant cylinder lubrication system for a large two-stroke internal combustion engine | |
| CN109642481B (en) | Cylinder oiling device and crosshead type internal combustion engine | |
| Murawski | Adjustment of cylinder lubricating oil of marine slow-speed engines | |
| CN102251895B (en) | Crosshead-shaped large uniflow-type dual-stroke diesel engine | |
| CN109469530A (en) | Internal combustion engine valve protector |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20171027 Termination date: 20200208 |