CN105569760A - Control method for quickly switching over a reciprocating piston engine - Google Patents
Control method for quickly switching over a reciprocating piston engine Download PDFInfo
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- CN105569760A CN105569760A CN201510657252.6A CN201510657252A CN105569760A CN 105569760 A CN105569760 A CN 105569760A CN 201510657252 A CN201510657252 A CN 201510657252A CN 105569760 A CN105569760 A CN 105569760A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/02—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for reversing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/028—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation for two-stroke engines
- F02D13/0284—Variable control of exhaust valves only
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2250/00—Engine control related to specific problems or objectives
- F02D2250/06—Reverse rotation of engine
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Valve Device For Special Equipments (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
Abstract
The invention relates to a control method for quickly switching over a reciprocating piston engine. The control method for quickly reversing or braking the rotation of a crank shaft of the reciprocating piston engine in a first rotary direction (the reciprocating piston engine being specially a low-speed operated uniflow scavenging type large-scale two-stroke diesel engine) includes the steps of: interrupting the fuel supply to the reciprocating piston engine in a brake phase, and providing a hydraulic media under a predetermined maximum opening pressure of a valve hydraulic device of a first exhaust valve of a first air cylinder at a first crank angle which is arranged in a region of a top dead center position of a first piston associated with the first cylinder. Therefore in a second crank angle, when the first piston passes through the top dead center position at first, the first exhaust valve is automatically opened through the valve hydraulic device.
Description
Technical field
The present invention relates to a kind of controlling method for the rotation in a first rotational direction of the bent axle of stroke piston combustion engine is reversed fast or braked, particularly, described internal-combustion engine is the uniflow scavenging formula large two-stroke diesel engine of low cruise, described internal-combustion reciprocating-pisto comprises cylinder, in described cylinder, piston is arranged to move around between the top dead center corresponding in the crankangle with 180 ° and the lower dead center corresponding respectively with the crankangle of 0 ° or 360 °, and described cylinder has exhaust valve, under predetermined cracking pressure, exhaust valve described in hydraulic medium hydraulic actuating is passed through by hydraulic valve device, described hydraulic medium is preferably hydraulic oil.
Background technique
Be often used as the driver element of steamer during large-scale diesel engine or be also used in fixing operation, such as, for driving the high-rating generator producing electric energy.In this, motor runs with ongoing operation as a rule in considerable time section, and this makes the requirement of operating security and usability high.In fueling interval long especially, therefore low-loss and economic manipulation of fuel and work materials are the central standard that operator operate machines.This piston operation action with the slow-running diesel engine of large cylinder bore diameter is fueling gap length, usability, oiling agent consumption, also direct for running cost therefore for the exhausted qualitative factor of operating efficiency, also has other factors.
In the transport of deep-sea, expect always and need in emergency situations within the time short as far as possible and therefore in distance short as far as possible by steamer braking at full speed or as quickly as possible by engine inversion, propulsion device is rotated as quickly as possible in the opposite direction, makes steamer can continue to navigate by water in the opposite direction immediately as far as possible.Although for relatively little motor ship or motor boat, variously to be proved to be effective process by applying widely for a long time and to have used for this purpose for a long time and often only can perform reversion by transmission device, " but emergency braking ", namely, fast braking from full speed is the problem be not solved to a great extent to the large ship being equipped with large-scale stroke piston combustion engine (such as, being equipped with the uniflow scavenging formula large two-stroke diesel engines of low cruise).Except the braking of steamer, this relates to and is inverted to the closely-related problem of contrary sense of rotation with motor fast from a sense of rotation.
For the uniflow scavenging formula large two-stroke diesel engines of low cruise, especially exist following cannot by the problem underestimated: because have these motors, due to large scale and the power of these motors, between motor and propulsion device, obviously use transmission device and/or clutch so discharged in practice, thus propulsion device is rotatably fixedly attached to the bent axle of the large-scale diesel engine in the steamer with this motor by axle.
Therefore compare compared to the driving arranging transmission device between propulsion device and motor, it is obviously simpler that the structure of this driving is known as ground.But, this not belt driver and the shortcoming of structure not with clutch are, propulsion device namely (always, under often kind of serviceability) be rotatably fixedly attached to motor and at least can not disconnect with motor under the serviceability (as long as that is, motor does not become the state stagnated completely) of motor.That is, at stopping motor with under the serviceability braking steamer (meaning the fuel supply in fact interrupted motor in essence), steamer does not just stop immediately then and there, but start most to continue navigation by due to its huge inertia, just little by little will lose speed gradually.
On this point, propulsion device is now considered to no longer by engine-driving; But it is driven by the lasting relative velocity between propulsion device and water, advances in water.But be rotatably fixedly attached to motor due to propulsion device and can not disconnect with motor, therefore motor is now also driven by propulsion device in such an operation state.This means, after stopping fuel supply, continuation but rotates up in original-party, because it is now driven by propulsion device by motor in considerable time section.
Can by means of only restarting motor in the reverse rotation direction to realize by steamer braking or by the acceleration of line direction reversion before steamer.For most of known ship engine, particularly for huge uniflow scavenging formula large two-stroke diesel engine, can by means of only at suitable time point (namely, crankangle with suitable) pressurized air (being also referred to as term " startup air ") is pushed down in cylinder liner at enough high pressure, making in piston, motor to be restarted by starting air effect on required counterrotating direction, realizing this acceleration.
Due to propulsion device by the enormous power that the piston of bent axle in the cylinder liner of described motor applies (as mentioned above, although described enormous power makes to stop supply fuel but motor continues to rotate up in original-party), so the earliest when start the maximum available pressure of air be enough to compensate propulsion device act on the power of piston time, motor then can restart in the opposite direction, rotate fast enough in the opposite direction under making motor can be provided in the effect starting air, so that motor can finally restart when restarting supply fuel in the opposite direction independently.When motor restarts in contrary sense of rotation, drive in the opposite direction under the effect of motor with the propulsion device that motor is rotatably fixedly connected with is naturally same, thus, the braking of steamer can be accelerated subsequently gradually, until moving ahead of steamer finally becomes stagnation, or as required, steamer can start to move ahead in the opposite direction.
Above-mentioned and before be apparent by the shortcoming of convention process of steamer braking and reversion.On the other hand, by steamer (especially, steamer with the uniflow scavenging formula large two-stroke diesel engine of low cruise) need the plenty of time, because before motor can restart in the opposite direction, first wait for a long time must be carried out, until steamer has been lost enough speed and become enough slow, the engine-driving of being undertaken by propulsion device has been made to be activated compensated with air.This still will spend considerable time length, and when steamer must be made in emergency situations reliably, immediately very fast to brake (such as, in order to prevent bumping against with iceberg, another obstacle or another steamer), this is a large shortcoming.Famous Titanic (Titanic) disaster allows people remember clearly so far, in this disaster, except other, can not be braked by steamer immediately.Even if Titanic is not driven by the uniflow scavenging formula large two-stroke diesel engine of low cruise, this problem is the same substantially.
When making like this to brake or be inverted to contrary before the distance entered of line direction hour wheel shipping agency reduce to minimum, often attempt by start to cylinder liner supply air and as far as possible in the time the earliest by engine inversion.But motor is driven by propulsion device thus runs faster on old direction, in order to start the reversion on opposite direction, startup air or the startup air energy of needs are more.Not only cost is high and be that energy ezpenditure is large for this, starts air because first-selection must use corresponding compressor to produce and must start air storage in pressure stored body.But the method also creates following risk: consume more or less startup air total stocks, it is but impossible that motor starts in the opposite direction.Not only be delayed braking further like this, and even can become security risk, because in this case, again must provide new and start air and motor can start no longer again simultaneously, lethal effect can be brought so in some cases, because steamer is not driven in this case.
Summary of the invention
Therefore, the object of this invention is to provide one can by motor (particularly, the uniflow scavenging formula large two-stroke diesel engine of low cruise) in the opposite direction more effectively and the method for reversing sooner, wherein, avoid the problem according to description of the prior art dramatically; Particularly, fatal safety problem well known in the prior art can be avoided and can economically and more save the reversion that energy ground performs motor in addition.
The feature meeting the theme of the present invention of these objects is: interrupt to described internal-combustion reciprocating-pisto supply fuel in the deboost phase, and when being arranged in first crankangle in region of top dead center position of the first piston associated with the first cylinder, described hydraulic medium is provided under the predetermined maximum cracking pressure of the hydraulic valve device of the first row valve of described first cylinder, make when the second crankangle, when described first piston is by described top dead center position, automatically open described first row valve by described hydraulic valve device.
Particularly advantageous mode of execution of the present invention is as follows:
In the first preferred embodiment, described second crankangle is after the top dead center of described first piston, in the scope between the top dead center and lower dead center of described first piston, the value of described second crankangle is between 180 ° and 360 °, preferably between 180 ° and 225 °, or between 180 ° and 200 °, particularly preferably between 180 ° and 190 °.
In the second preferred implementation, during the 3rd crankangle in the region between described second crankangle and the lower dead center of described first piston, more closed described first row valve, to produce predetermined vacuum in described first cylinder.
In the 3rd preferred implementation, in the described deboost phase of the rotation of described first sense of rotation, described 3rd crankangle is selected at described stroke piston combustion engine, make by closing described first row valve when described 3rd crankangle, in described first cylinder, produce vacuum, thus the braking of the rotation of described stroke piston combustion engine in described first sense of rotation is obtained to the auxiliary of the vacuum produced.
In the 4th preferred implementation, described 3rd crankangle is selected in the reversion stage of the described stroke piston combustion engine after the described deboost phase, make by closing described first row valve when described 3rd crankangle, in described first cylinder, produce vacuum, thus described stroke piston combustion engine the restarting in second sense of rotation contrary with described first sense of rotation inspired by supplying fuel in the second cylinder obtains the auxiliary of the vacuum produced in described first cylinder.
In the 5th preferred implementation, when the four-throw angle between described lower dead center and described top dead center, during the four-throw angle preferably reached after stopping being fed in described cylinder by scavenging air, closed described first row valve.
In the 6th preferred implementation, described four-throw angle is selected in the described deboost phase of the rotation of described stroke piston combustion engine, make by closing described first row valve when described four-throw angle, in described first cylinder, produce excessive pressure, thus the braking of the rotation of described stroke piston combustion engine in described first sense of rotation is obtained to the auxiliary of the excessive pressure produced.
In the 7th preferred implementation, described four-throw angle is selected in the reversion stage of the described stroke piston combustion engine after the described deboost phase, make by closing described first row valve when described four-throw angle, in described first cylinder, produce excessive pressure, thus described stroke piston combustion engine the restarting in second sense of rotation contrary with described first sense of rotation inspired by supplying fuel in the second cylinder obtains the auxiliary of the excessive pressure produced in described first cylinder.
In the 8th preferred implementation, the described stroke piston combustion engine inspired during the reversion stage restarting in described second sense of rotation contrary with described first sense of rotation obtains following assisting, and is about to predetermined minimum startup air and introduces at least one cylinder of described stroke piston combustion engine.
In the 9th preferred implementation, described startup air is sequentially only introduced in some cylinders of described stroke piston combustion engine, preferably, even only introduce in selected single cylinder, and do not introduce in other any cylinder, to assist restarting during the described reversion stage in described second sense of rotation.
In the tenth preferred implementation, the described stroke piston combustion engine inspired during the described reversion stage restarting in described second sense of rotation contrary with described first sense of rotation occurs when not using and starting air.
In the 11 preferred implementation, described stroke piston combustion engine is the driver element of steamer.
Therefore, the present invention relates to a kind of controlling method for the rotation in a first rotational direction of the bent axle of internal-combustion reciprocating-pisto is reversed fast or braked, the uniflow scavenging formula large two-stroke diesel engine of described internal-combustion reciprocating-pisto specifically low cruise, described internal-combustion reciprocating-pisto comprises cylinder, in described cylinder, piston is arranged to move around between the top dead center corresponding in the crankangle with 180 ° and the lower dead center corresponding respectively with the crankangle of 0 ° or 360 °, and described cylinder has exhaust valve, can pass through with hydraulic medium hydraulic actuating exhaust valve under predetermined cracking pressure by hydraulic valve device, described hydraulic medium is preferably hydraulic oil.According to the present invention, in the deboost phase, interrupt to described internal-combustion reciprocating-pisto supply fuel, and when being arranged in first crankangle in region of top dead center position of the first piston associated with the first cylinder, hydraulic medium is provided under the predetermined maximum cracking pressure of the hydraulic valve device of the first row valve of described first cylinder, make when the second crankangle, when described first piston is by described top dead center position, automatically open described first row valve by described hydraulic valve device.
The present invention provides one first can by motor (particularly, the uniflow scavenging formula large two-stroke diesel engine of low cruise) more effectively and be inverted to the method that contrary sense of rotation can save valuable startup air in addition simultaneously more quickly.According in the particularly preferred mode of execution of method of the present invention, such as, while make use of propulsion device and being supplied to the braking energy of motor, even in steamer, restarting in contrary sense of rotation can be inspired without any when startup air completely, when being used for the engine inversion of steamer or braking according to method of the present invention, this not only naturally represents and by the improvement underestimated, and cannot especially also represent the huge advance of safety technique aspect in urgent.
Actually in particularly preferred mode of execution, stroke piston combustion engine is the uniflow scavenging formula large two-stroke diesel engine of the low cruise of steamer, described steamer is such as the container ship with huge motor, described huge motor has such as a nearly ten two or more cylinder and each cylinder has power up to 10,000kW or even larger power.
As those skilled in the art itself knows, move around between top dead center in cylinder liner of the normal operating state lower piston of internal-combustion reciprocating-pisto and lower dead center, and piston by the bent axle be operationally fixedly connected with piston and propulsion device to drive propulsion device.By to carry out the exhaust valve in the cylinder head of hydraulic starting cylinder liner by hydraulic valve device with programmable control unit, in fact programmable control unit can comprise hydraulic pressure installation and electronic equipment.On this point, the crankangle starting exhaust valve corresponding can be made a reservation for by programmable control unit in essence as required.Start air valve come from dead state ato unit by activating, otherwise can under enough less rotational speeies ato unit, change the sense of rotation of motor.
Embodiment
In order to understand the present invention better, below by the general operation pattern again briefly, under the normal operating state of the schematically stroke piston combustion engine that review itself is known.In the framework of the application, the crankangle of 0 ° or 360 ° represents with lower dead center UT respectively and the crankangle of 180 ° represents with top dead center OT.
From corresponding to the lower dead center of 0 ° of crankangle, first piston moves in operational conditions on the direction OT corresponding to 180 ° of crankangles.When piston is positioned at the position near lower dead center, in the lower area of cylinder liner, unclamps scavenging slit and open exhaust valve under normal operating condition.As long as piston unclamps scavenging slit, fresh air just by scavenging slit be supplied to cylinder liner combustion space and simultaneously because piston disposes combustion residue moving up towards the side of top dead center from combustion space.When piston makes to no longer include any connection between combustion space and scavenging slit by scavenging slit completely, along with crankangle increases, pass through control gear closed row valve by predetermined crankangle place.In other process, with the combustion space supply fuel of injection valve to the motor formed by upper cylinder region, the cylinder head being positioned at upper cylinder overlying regions and piston base, described fuel is lighted by the air that heats because of compression in the region of top dead center, with after-combustion and produce power, increased by this energy release pressure in combustion space.
By after top dead center, piston is moving up towards the side of lower dead center of the crankangle corresponding to 360 ° again.Under the normal running and forward traveling of steamer, then again open exhaust valve and correspond to the crankangle startup new round cylinder operation cycle more much bigger than 180 °.
At steamer by when being braked, especially, when should in an emergency situation at distance inside brake steamer short as far as possible time, also stroke piston combustion engine is arranged to carry out the different operating state of braking or reversing with known method.In a first step, it is known that interrupt supplying fuel in the cylinder liner of stroke piston combustion engine.Supplied by interrupts fuel, first the rotational speed achieving motor reduces, this cause steamer first appropriateness slow down.If do not take other measure, then due to the friction of steamer in water, the speed of steamer significantly reduces.This friction is usually quite little, and the speed of steamer only slowly is reduced.No longer now driven by the kinetic energy that steamer still exists by the propulsion device that stroke piston combustion engine drives after interrupts fuel supply, operate as turbo machine, and now drive the motor that described propulsion device is rotatably fixedly connected with by bent axle.
If now keep the control of exhaust valve constant as put into practice before in prior art as in normal running, then the part being known as steamer kinetic energy is converted into the compression energy in the cylinder of crank angle range between 0 ° and 180 °; But, during piston moves to lower dead center from top dead center, during the scavenging air follow-up expansion comprised in cylinder liner, again turn back to steamer by almost complete for this compression energy with kinetic energy form by propulsion device.
The present invention is now from this point and be based on following understanding: substantially motor can be reversed fast or brake only by suitably controlling exhaust valve, and in fact can in particular even when being not activated air and at least there is the few startup air than needing in prior art before, restart in the opposite direction, prerequisite employs according to the present invention the braking energy being delivered to motor by propulsion device dexterously.
In the preferred implementation according to control procedure of the present invention, second crankangle is chosen to be after the top dead center of first piston, in the scope between the top dead center and lower dead center of first piston, the value of the second crankangle is between 180 ° and 360 °, preferably between 180 ° and 225 °, or between 180 ° and 200 °, particularly preferably between 180 ° and 190 °.
In order to obtain the further improvement of braking effect when reversing, during the 3rd crankangle in the region between the second crankangle and the lower dead center of first piston, more closed first row valve, to produce predetermined vacuum in the first cylinder.
According to reversion stage of motor of taking this measure, two kinds of good effects substantially can be produced.
And if produce the corresponding selection of vacuum the 3rd crankangle if performed in deboost phase of rotating in a first rotational direction of stroke piston combustion engine in the first cylinder, then can by the closed row valve when suitable selection the 3rd crankangle, in the first cylinder, produce vacuum, make to obtain the auxiliary of the vacuum produced to the braking of stroke piston combustion engine rotation in a first rotational direction.Thus, cause at least slight suction effect to piston thus, make to cause the correspondence to piston movement to brake, eliminate kinetic energy from motor in addition like this, therefore accelerate braking.
On the other hand, can also after the deboost phase, the 3rd crankangle is selected in the reversion stage of stroke piston combustion engine, make by closing first row valve when the 3rd crankangle, in the first cylinder, produce vacuum, thus in second sense of rotation contrary with the first sense of rotation, restart the auxiliary of the vacuum obtaining producing in the first cylinder by the stroke piston combustion engine inspired at the second cylinder supply fuel.This means, because the first sense of rotation relative to motor creates braking suction effect in the first cylinder, therefore motor restart (that is, the reversion of motor in the second new sense of rotation of the motor contrary with the first sense of rotation) facilitated or assisted, make it possible to become more early reversion, or likely also make required startup air minimum or exempted from startup air even completely.
When being included in the four-throw angle between lower dead center and top dead center according to other extra or alternative measure of method of the present invention, during the four-throw angle preferably reached after stopping being fed in cylinder by scavenging air, closed first row valve.
Namely use the measure of finally specifying, situation is, according to performing the exhaust valve closed engine inversion stage at four-throw angle place, can produce other two kinds of good effects substantially.
On the one hand, when selecting four-throw angle to make by closing first row valve during at four-throw angle produce excessive pressure in the first cylinder in the deboost phase of the rotation of stroke piston combustion engine, the braking of stroke piston combustion engine rotation is in a first rotational direction obtained to the auxiliary of the excessive pressure produced.In fact, because cause due to the pressure produced in cylinder eliminating kinetic energy (this is because kinetic energy is converted into pressure energy) from motor, so motor braking in a first rotational direction obtains very effective auxiliary thus.
On the other hand, in the reversion stage of the stroke piston combustion engine after the deboost phase, select four-throw angle to make to produce excessive pressure by closing first row valve at four-throw angle place in the first cylinder, stroke piston combustion engine the restarting in second sense of rotation contrary with the first sense of rotation making the excessive pressure that produces in the first cylinder and inspire by supply fuel carry out suitable when engaged, restarting in contrary sense of rotation can obtain effectively assisting of the excessive pressure produced in the first cylinder.
This means, because the first sense of rotation relative to motor produces retardation pressure effect in the first cylinder, therefore motor restart (namely, the reversion of motor in the second sense of rotation that the motor contrary with the first sense of rotation is new) facilitated or assisted, make it possible to more early reversion, or required startup air likely also can be made minimum or exempted from startup air even completely.
Particularly, if when reverse particularly rapidly occur or when such as steamer needs emergency braking or exist need quickly to perform other situations according to method of the present invention time, the stroke piston combustion engine inspired during the reversion stage restarting in second sense of rotation contrary with the first sense of rotation can obtain following assisting naturally in addition, being about to predetermined minimum startup air introduces at least one cylinder of stroke piston combustion engine, thus, also can accelerate the braking being inverted to the second sense of rotation or accelerating the first sense of rotation.
Particularly (but moreover), when need unlike in emergency circumstances very fast process time, also sequentially only can introduce starting air in some cylinders of stroke piston combustion engine, preferably, even only introduce in selected single cylinder, and do not introduce in other any cylinder, to assist during the reversion stage restarting in a second rotational direction.
The stroke piston combustion engine even allowing (as already mentioned above) to inspire during the reversion stage according to method of the present invention restarting in second sense of rotation contrary with the first sense of rotation does not occur when completely not using and start air, this is because control exhaust valve very dexterously, make to employ the kinetic energy feeding back to motor under angle of rake effect ideally.
In fact, stroke piston combustion engine has multiple cylinder, and (described multiple cylinder is arranged in a way known, in all cases at one time under be in different crank shaft angle at least partly), make to take to mention here simultaneously for the braking of booster engine or the measure of reversion, make the additive effect producing different measure.
Be appreciated that the embodiments of the present invention described in the application also can combine by any suitable method independent of the application, described particular implementation is only interpreted as citing.Technician recognizes other improvement simply favourable of described embodiments of the present invention immediately, and understands the present invention and naturally also contemplated these other improvement simple.
Claims (12)
1. the controlling method for the rotation in a first rotational direction of the bent axle of internal-combustion reciprocating-pisto is reversed fast or braked, the uniflow scavenging formula large two-stroke diesel engine of described internal-combustion reciprocating-pisto specifically low cruise, described internal-combustion reciprocating-pisto comprises cylinder, in described cylinder, piston is arranged to move around between the top dead center corresponding in the crankangle with 180 ° and the lower dead center corresponding respectively with the crankangle of 0 ° or 360 °, and described cylinder has exhaust valve, under predetermined cracking pressure, exhaust valve described in hydraulic medium hydraulic actuating is passed through by hydraulic valve device, described hydraulic medium is preferably hydraulic oil, it is characterized in that, in the deboost phase, interrupt to described internal-combustion reciprocating-pisto supply fuel, and when being arranged in first crankangle in region of top dead center position of the first piston associated with the first cylinder, described hydraulic medium is provided under the predetermined maximum cracking pressure of the hydraulic valve device of the first row valve of described first cylinder, make when the second crankangle, when described first piston is by described top dead center position, described first row valve is automatically opened by described hydraulic valve device.
2. controlling method according to claim 1, wherein, described second crankangle is after the top dead center of described first piston, in the scope between the top dead center and lower dead center of described first piston, the value of described second crankangle is between 180 ° and 360 °, preferably between 180 ° and 225 °, or between 180 ° and 200 °, the second crankangle particularly preferably between 180 ° and 190 °.
3. controlling method according to claim 1 and 2, wherein, during the 3rd crankangle in the region between described second crankangle and the lower dead center of described first piston, more closed described first row valve, to produce predetermined vacuum in described first cylinder.
4. controlling method according to claim 3, wherein, in the described deboost phase of the rotation of described first sense of rotation, described 3rd crankangle is selected at described stroke piston combustion engine, make by closing described first row valve when described 3rd crankangle, in described first cylinder, produce vacuum, thus the braking of the rotation of described stroke piston combustion engine in described first sense of rotation is obtained to the auxiliary of the vacuum produced.
5. controlling method according to claim 3, wherein, described 3rd crankangle is selected in the reversion stage of the described stroke piston combustion engine after the described deboost phase, make by closing described first row valve when described 3rd crankangle, in described first cylinder, produce vacuum, thus described stroke piston combustion engine the restarting in second sense of rotation contrary with described first sense of rotation inspired by supplying fuel in the second cylinder obtains the auxiliary of the vacuum produced in described first cylinder.
6. according to controlling method in any one of the preceding claims wherein, wherein, when the four-throw angle between described lower dead center and described top dead center, during the four-throw angle preferably reached after stopping being fed in described cylinder by scavenging air, closed described first row valve.
7. controlling method according to claim 6, wherein, described four-throw angle is selected in the described deboost phase of the rotation of described stroke piston combustion engine, make by closing described first row valve when described four-throw angle, in described first cylinder, produce excessive pressure, thus the braking of the rotation of described stroke piston combustion engine in described first sense of rotation is obtained to the auxiliary of the excessive pressure produced.
8. controlling method according to claim 6, wherein, described four-throw angle is selected in the reversion stage of the described stroke piston combustion engine after the described deboost phase, make by closing described first row valve when described four-throw angle, in described first cylinder, produce excessive pressure, thus described stroke piston combustion engine the restarting in second sense of rotation contrary with described first sense of rotation inspired by supplying fuel in the second cylinder obtains the auxiliary of the excessive pressure produced in described first cylinder.
9. according to controlling method in any one of the preceding claims wherein, wherein, the described stroke piston combustion engine inspired during the reversion stage restarting in described second sense of rotation contrary with described first sense of rotation obtains following assisting, and is about to predetermined minimum startup air and introduces at least one cylinder of described stroke piston combustion engine.
10. controlling method according to claim 9, wherein, described startup air is sequentially only introduced in some cylinders of described stroke piston combustion engine, preferably, even only introduce in selected single cylinder, and do not introduce in other any cylinder, to assist restarting during the described reversion stage in described second sense of rotation.
11. controlling methods according to any one of claim 1 to 8, wherein, the described stroke piston combustion engine inspired during the described reversion stage restarting in described second sense of rotation contrary with described first sense of rotation occurs when not using and starting air.
12. according to controlling method in any one of the preceding claims wherein, and wherein, described stroke piston combustion engine is the driver element of steamer.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP14191349 | 2014-10-31 | ||
| EP14191349.1 | 2014-10-31 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105569760A true CN105569760A (en) | 2016-05-11 |
| CN105569760B CN105569760B (en) | 2019-11-12 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510657252.6A Active CN105569760B (en) | 2014-10-31 | 2015-10-13 | Control method for quickly inverting reciprocating piston internal combustion engine |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP3015663B1 (en) |
| JP (1) | JP6807150B2 (en) |
| KR (1) | KR102390243B1 (en) |
| CN (1) | CN105569760B (en) |
| DK (1) | DK3015663T3 (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB190927736A (en) * | 1909-11-29 | 1910-07-21 | Alexander Pearson Maclaren | Improvements relating to Motor Boats. |
| DE895550C (en) * | 1943-01-05 | 1953-11-05 | Fried Krupp Germaniawerft Ag | Device for braking internal combustion engines, in particular reversible marine propulsion engines |
| GB722568A (en) * | 1951-09-27 | 1955-01-26 | Suedwerke Motoren Und Kraftwag | Valve gear for two-stroke uniflow scavenging engines to facilitate braking |
| US4226216A (en) * | 1976-09-30 | 1980-10-07 | Societe D'etudes De Machines Thermiques S.E.M.T. | Method of quick pneumatic braking of a diesel engine |
| KR20050060985A (en) * | 2003-12-17 | 2005-06-22 | 정영섭 | Method for braking a ship utilizing engine and braking device thereof |
| WO2006122570A1 (en) * | 2005-05-13 | 2006-11-23 | Daimlerchrysler Ag | Two-stroke engine braking process for a supercharged internal combustion engine |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0521139U (en) * | 1991-09-03 | 1993-03-19 | 三菱重工業株式会社 | Rotational braking system for 2-cycle large diesel engine |
| DE19825411C1 (en) | 1998-06-06 | 1999-10-07 | Daimler Chrysler Ag | Reversible reciprocating internal combustion engine, e.g. for motor vehicles esp. in reverse gear |
| DE50008185D1 (en) | 1999-04-30 | 2004-11-18 | Waertsilae Nsd Schweiz Ag | Method and device for starting, braking and reversing a two-stroke diesel engine |
| JP3795425B2 (en) | 2001-04-26 | 2006-07-12 | エムエーエヌ・ビー・アンド・ダブリュ・ディーゼル・エーエス | Process for braking and reversing an internal combustion engine |
| TW555934B (en) * | 2001-10-24 | 2003-10-01 | Yamaha Motor Co Ltd | Engine start control method and device |
| JP2009008025A (en) | 2007-06-28 | 2009-01-15 | Denso Corp | Control device for internal combustion engine |
| JP4825786B2 (en) | 2007-12-20 | 2011-11-30 | 本田技研工業株式会社 | 4-cycle engine stroke discrimination device |
-
2015
- 2015-09-08 EP EP15184261.4A patent/EP3015663B1/en active Active
- 2015-09-08 DK DK15184261.4T patent/DK3015663T3/en active
- 2015-10-13 CN CN201510657252.6A patent/CN105569760B/en active Active
- 2015-10-16 JP JP2015204151A patent/JP6807150B2/en active Active
- 2015-10-16 KR KR1020150145002A patent/KR102390243B1/en active IP Right Grant
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB190927736A (en) * | 1909-11-29 | 1910-07-21 | Alexander Pearson Maclaren | Improvements relating to Motor Boats. |
| DE895550C (en) * | 1943-01-05 | 1953-11-05 | Fried Krupp Germaniawerft Ag | Device for braking internal combustion engines, in particular reversible marine propulsion engines |
| GB722568A (en) * | 1951-09-27 | 1955-01-26 | Suedwerke Motoren Und Kraftwag | Valve gear for two-stroke uniflow scavenging engines to facilitate braking |
| US4226216A (en) * | 1976-09-30 | 1980-10-07 | Societe D'etudes De Machines Thermiques S.E.M.T. | Method of quick pneumatic braking of a diesel engine |
| KR20050060985A (en) * | 2003-12-17 | 2005-06-22 | 정영섭 | Method for braking a ship utilizing engine and braking device thereof |
| WO2006122570A1 (en) * | 2005-05-13 | 2006-11-23 | Daimlerchrysler Ag | Two-stroke engine braking process for a supercharged internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105569760B (en) | 2019-11-12 |
| EP3015663B1 (en) | 2018-11-07 |
| JP2016089825A (en) | 2016-05-23 |
| JP6807150B2 (en) | 2021-01-06 |
| KR102390243B1 (en) | 2022-04-22 |
| EP3015663A1 (en) | 2016-05-04 |
| KR20160051607A (en) | 2016-05-11 |
| DK3015663T3 (en) | 2019-03-04 |
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