CN1302944A - Air change system of internal combustion engine and operating method of said air change system - Google Patents
Air change system of internal combustion engine and operating method of said air change system Download PDFInfo
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- CN1302944A CN1302944A CN01101388A CN01101388A CN1302944A CN 1302944 A CN1302944 A CN 1302944A CN 01101388 A CN01101388 A CN 01101388A CN 01101388 A CN01101388 A CN 01101388A CN 1302944 A CN1302944 A CN 1302944A
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- valve
- fluid system
- main control
- scavenging air
- piston
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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
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
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- 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
- F02F7/00—Casings, e.g. crankcases or frames
- F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines
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- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
The gas change system for an internal combustion motor, such as a diesel motor, has a hydraulically operated gas change valve 20 linked to an initial fluid system 30 for a medium to operate the valve 20. A second fluid system 40 for a hydraulic medium has a main control valve 50 to control the gas change valve 20. A medium separator 70 is between the main control valve 50 and the gas change valve 20, where one side is linked to the initial fluid system 30 and the other side is connected to the second fluid system 40.
Description
The present invention relates to the air exchange system that independent claims a kind of internal-combustion engine as described in the preamble separately uses and the method for work of this air exchange system.
The device that is used for the outlet valve of hydraulic driving one internal-combustion engine is disclosed in EP-A-0539320.The valve body of this outlet valve drives by a servopiston that is connected on the hydraulic control device.This hydraulic control device comprises one by a solenoid actuated and drive the pilot valve of a control valve.In addition, a liquid-storage container is set, this hydraulic medium is kept in this liquid-storage container with certain pressure.In order to open this outlet valve, this control valve switches to a position that the fluid connection between this liquid-storage container and the servopiston is opened by the respective drive of this pilot valve, so this servopiston is full of the hydraulic medium that has pressure, and make valve body move to the enable possition.In order to close outlet valve, this control valve switches to the position that the connection that makes between this liquid-storage container and this servopiston is communicated with cut-out by the respective drive of this pilot valve, and simultaneously, this position can make and cut off flowing of this hydraulic medium, thereby makes this servopiston pressure release.
Although verified in practice this device is valuable, also there is shortcoming in it.For example in maintaining or when maintenance, it must the removal cylinder head, so hydraulic system must be opened.So just produced the very big danger that can pollute this hydraulic system, this hydraulic system is normally kept clean by fine mesh filter.This pollution particularly can produce infringement to this pilot valve and control valve, and this will improve maintenance cost greatly.Because all cylinders of this motor link to each other with same hydraulic system, even therefore only need open a cylinder head, this danger also can be present in all cylinders.This motor in addition, also can have such danger, promptly can produce leakage, thereby influence whole hydraulic system, so that can not be restarted at assembly process.
From the prior art, the objective of the invention is for a kind of air exchange system and a kind of method that makes this air exchange system work are provided, the described shortcoming of prior art no longer exists in this method.Therefore this air exchange system particularly can not make this hydraulic system to the maintenance or the nursing of single cylinder, and particularly there is contaminated danger in the hydraulic system of this pilot valve and control valve.
The theme of realizing the apparatus and method of purpose of the present invention is embodied in the described feature of independent claims of each respective type.
Therefore, the internal-combustion engine of the present invention's proposition comprises with air exchange system: a hydraulic driving scavenging air valve and a first fluid system that is used for a working medium, this fluid system is connected on this scavenging air valve, is used to drive this scavenging air valve.This air exchange system also comprises second fluid system that is used for a hydraulic medium, one is arranged on the main control valve that is used to drive this scavenging air valve in this second fluid system, and dielectric separator that is arranged between this main control valve and this scavenging air valve, one end of this separator is connected in this first fluid system, and the other end is connected on this second fluid system.
By the measure of two fluid systems that separated by a dielectric separator is set, thereby may be to single cylinder place under repair or maintenance, and do not need to open second fluid system that has this main control valve, so there is not the danger of polluting or leaking in this second fluid system.In addition, also might each single cylinder and this internal-combustion engine be disconnected by this measure, so an internal-combustion engine that has n cylinder still can continue operation under the situation of (n-1) individual cylinder, and maintenance work can be carried out in the cylinder that disconnects.
In optimizing embodiment, this main control valve comprises: a control piston with an enable possition and a closed position, and when this internal-combustion engine normally moved, this enable possition was opened this scavenging air valve simultaneously, and this closed position is closed this scavenging air valve.This main control valve also comprises a spring element that is provided with by following mode, and promptly this spring applies the power towards closed position for this control piston, and this moves to the enable possition with regard to meaning the elastic force that this control slider must head on this spring element.If do not have pressure in this second fluid system, then this spring element can guarantee that this control slider moves to closed position or is maintained in its closed position.Therefore this spring element produces a biasing force in the direction of the closed position of this control piston.This has just brought such advantage, promptly specifically, when this internal combustion engine start, when the pressure in this second fluid system is set up, can avoid this scavenging air valve to produce undesirable unlatching in short-term effectively.
To the internal-combustion engine (saying there is not Control Shaft on traditional sense) that electronic control or electricity-liquid jointly control, its advantage provides in second fluid system of this air exchange system a solenoid pilot valve is set, and is used to guide this main control valve.Like this, just may be respectively by means of automatically controlled pulse or this air exchange system of electronic control pulsed drive.
In addition, more advantageously this scavenging air valve has a driven plunger, and this piston can form a step piston that is used to drive this scavenging air valve.Be that hydraulic energy can obtain saving by this measure.
In addition, the invention allows for a kind of method that makes the air exchange system work in the internal-combustion engine, in described method, one scavenging air valve passes through a working medium by the first fluid system drive, this first fluid system has one by a main control valve that is used for second fluid system driving of a hydraulic medium and is used to control this scavenging air valve, and effective connection that between this first and second fluid system, forms by a dielectric separator, this separator is arranged between this main control valve and the scavenging air valve, and the one end is connected in this first fluid system, and the other end is connected on this second fluid system.
For already mentioned reason, when this method of consideration, be preferably and make this main control valve apply an elastic force by a spring element in the direction of the closed position of this control piston, when the normal operating condition of this internal-combustion engine, described closed position is closed this scavenging air valve.
Method embodiment of the present invention is particularly advantageous to the internal-combustion engine that electronic control or electric liquid jointly control, and wherein this main control valve is by means of a solenoid pilot valve guiding that has a magnetic slider, and this slider can switch between two electromagnet back and forth.
Optimize embodiment according to one of this method, need carry out following each step in order to drive this pilot valve:
One of two electromagnet of-driving,
The beginning of the motion of this magnetic slider of-detection; And
-from this magnetic slider setting in motion later in case when one preferably over and done with corresponding to the time lag of switching time of this pilot valve in fact, just make this electromagnet lose excitation.
By this measure, can guarantee that driven time of each electromagnet can be than not long in order to obtain the reliable needed time of handoff procedure.This point consider this pilot valve be subjected to the safety in operation of thermal process and this pilot valve the time be particularly advantageous.
Another favourable measure is by a predetermined pulse this pilot valve to be switched to an assigned position before this internal combustion engine start, and this assigned position is preferably corresponding to the closed position of this scavenging air valve.So just can guarantee that this scavenging air valve can not produce undesirable driving during this internal combustion engine start.
Air exchange system of the present invention and method of the present invention are particularly suitable for large-scale diesel engine, for example as boats and ships or produce the drive train etc. of the power station of electric power.This air exchange system and method also agree to be suitable for by pure automatically controlled mode or electric liquid jointly control that mode is controlled, promptly do not establish the large-scale diesel engine of the Control Shaft that is used for one control air valve and Fuelinjection nozzle.
Other favourable measure of the present invention and optimization embodiment can draw from each dependent claims.
Below, referring to each embodiment and each accompanying drawing device of the present invention and technological method are elaborated.The schematic representation that illustrates does not below draw by dimension scale, and they are:
Fig. 1 is the embodiment's of an air exchange system of the present invention partial sectional view,
Figure 1A is the enlarged view of the described details of Fig. 1,
The sectional view of Fig. 2 one large-scale diesel engine,
Fig. 3 is the rough schematic of a pilot valve, and
Fig. 4 is the driving schematic representation of this pilot valve of expression.
Fig. 1 represents an optimization embodiment's of air exchange system of the present invention partial sectional view, and its integral body is by label 10 expressions.This air exchange system comprises: one is the scavenging air valve of diesel exhaust valve 20 herein, a first fluid system 30 and second fluid system 40 that hydraulic medium is used that working medium is used.The liquid-storage container 41 of one main control valve, 50, one pilot valves 60 and a stores hydraulic pressure medium is arranged in this second fluid system 40.One dielectric separator 70 is arranged between main control valve 50 and the outlet valve 20, and an end of this separator 70 is connected in this first fluid system 30, and the other end is connected on this second fluid system 40.Make realization work connection between this first and second fluid system by this dielectric separator 70.
Figure 1A represents main control valve 50, the zoomed-in view of pilot valve 60 and dielectric separator.
Below with reference to the concrete Application Example of explanation air exchange system, wherein this air exchange system 10 is as the part of an automatically controlled large-scale diesel engine 1 (Fig. 2), and this diesel engine for example can be used as the drive train of boats and ships or power station.For the ease of understanding, Fig. 2 is schematically illustrated: this large-scale diesel engine 1 has one group of cylinder 2 commonly used.This large-scale diesel engine 1 is designed to have uniflow scavenged low speed two-stroke cross head type large-scale diesel engine, and this diesel engine is jointly controlled by electric control or electro-hydraulic, this just mean it typically be not used to take a breath and the mechanical-hydraulic type of oil spout control meaning on Control Shaft.
In these motors, this hydraulic system can be by the control of each pilot valve, and each pilot valve is driven by the electrical signal that comes from a control gear simultaneously, can carry out oil spout by means of this hydraulic system, ventilation, and can make suitable auxiliary system work such as start-up system.This control gear is by crankshaft angles, engine speed and other possible further state variables are determined, and give each pilot valve with automatically controlled signal, drive corresponding hydraulic system then, these variablees can be course of injection ideal time at interval and desirable fuel injection quantity, the opening and closing time point of outlet valve.By this very effective multifunction electric-hydraulic combined control, owing to no longer have the mechanical connection annex between each position of piston and the position of the driving element such as Injection Pump or stroke pump, so in all operating conditionss of this large-scale diesel engine, oil spout and gas exchange process all can be optimized by open-and-shut mode, and are suitable for each work cycle of this machinery.
This large-scale diesel engine 1 (Fig. 2) has a bent axle 3, this bent axle drives this gear 3a and a high-pressure service pump 5 meshed gears 4 by a crankshaft gear 3a and one, this high-pressure service pump 5 provides fuel under the pressure up to for example 2000 crust, entering one by oil circuit 6 provides one not have the oil sump tank 7 of injection system of detailed description at this.One pump 8 is set in addition, and this pump can drive and make hydraulic medium by bent axle 3, and the oil of for example a kind of hydraulic oil or control oil and so on enters the liquid-storage container 41 of this second fluid system by a pipeline 42.Nature, one can be provided with one group of high pressure oil pump 5 and/or one group of pump 8 that is used to provide hydraulic medium that is used to provide fuel.
Oil sump tank 7 and liquid-storage container 41 always form the tubular member that extends along motor.
The supply pipeline 43 that has a stop valve 44 is connected on this liquid-storage container 41.Behind stop valve 44, this supply pipeline branches into the branch road 43b in branch road 43a that is connected on this pilot valve 60 and the import 51 that is connected to this main control valve 50.The output of this pilot valve 60 is connected in the control import 52 of this main control valve 50 by a pipeline 65.
Fig. 3 represents an embodiment's of this pilot valve 60 rough schematic, and this pilot valve constitutes bistable state 3/2 three-way electromagnetic valve that is in the sliding motion structure.This pilot valve 60 comprises solenoid valve slider 62, and this slider is designed to a hollow cylinder member, has a neutral relief hole 621, and is arranged on movably in the housing 61.In this housing 61, be provided with a supply passage 63, one return flow lines 64 and and consume passage 66.This neutrality relief hole 621 is connected on this return flow line by each transverse holes 641.This supply passage 63 is connected on the branch road 43a of this supply pipeline 43, this return flow line 64 is connected on the pipeline 47 that extends to the return-flow system 49 that this hydraulic medium uses, and this consumption passage 66 is connected on the pipeline 65 of the control import 52 that extends to this main control valve 50.
This solenoid valve slider 62 can be by two electromagnet 67a, and the 67b effect is switched between the two positions back and forth, simultaneously this supply passage 63 and consume first-class between the passage 66 to be automatically connected in the primary importance place of this valve slider 62 shown in Figure 3 open-minded.At second place place, this consumption passage 66 is connected on this return flow line 64.
In order to make this pilot valve 60 as far as possible promptly switch to the another location from a position, promptly life period does not postpone, this electromagnet 67a, 67b has low-down inductance, and this can obtain by winding body the least possible by the quantity that makes winding and the low eddy current loss of use.This pilot valve 60 switches to the needed time of another position from a position, and promptly the amount of switching time for example is 0.5 millisecond.In addition, be a constant this switching time, and this just means it is repeatably to a great extent.To discuss to the action of this pilot valve 60 below.
This main control valve 50 has a control piston 56, and this piston has enable possition and the closed position shown in Fig. 1 and 1A.As following the explanation, when motor 1 normal operation, this enable possition is opened this outlet valve 20, and this closed position is closed this outlet valve 20.This main control valve 50 comprises that also one first connects 53 in addition, one second connects 54, one return port 55, by these two connections, this main control valve 50 is connected on this dielectric separator 70, by this return port, this hydraulic medium can flow out and flow into and be provided with the pipeline 47 of a stop valve 45 from this main control valve 50.This pipeline 47 is connected to this hydraulic medium with on this return-flow system 49.Therefore this main control valve 50 is one 4/2 logical valves herein.
This control piston 56 is by a spring element 57 controls, and this spring element is to be provided with like this, so that its elastic force attempts to shift this control piston 56 onto closed position or this piston is maintained in its closed position.Utilize this biasing force, can guarantee under the state of the pressure loss, promptly when it was not full of the hydraulic medium of band pressure, this control piston 56 was in the closed position respectively or be maintained in its closed position.Therefore this control piston 56 must be resisted this elastic force and move to the enable possition.Among the described herein embodiment, this spring element 57 forms a helical spring, and on the upper-end surface of this control piston 56 that an end bearing of this spring is shown in the figure, the other end is bearing on the housing of this main control valve 50.The end face of this control piston 56 is acted on by spring element 57, and is connected on this return port 55 by a center hole when this control piston is in the closed position, flows out then so flow into the hydraulic medium in the space between this end face and the housing.
This dielectric separator 70 comprises an isolation piston 72 that is arranged in the housing 73, and an end face 721 of this piston, i.e. the chamber 71 that the working medium of this first fluid system of the connection of the top shown in the figure is used.Both feed this dielectric separator 70 according to 721 belows, upper-end surface of figure this isolation piston that is shown in the connecting passage that links to each other with main control valve 50 53,54.Therefore this isolation piston 72 separates the working medium of this first fluid system working medium with this second fluid system.As shown in the figure, above this end face 721, the chamber 71 of this dielectric separator 70 is connected in this first fluid system 30 by a hole 74.
The first fluid system that this working medium is used comprises that a hole 74 with this dielectric separator 70 is connected to the pressure piping 31 on this outlet valve 20, the supply pipeline of using with this working medium 32, this supplying pipe one end is connected on this pressure piping 31 by a stop valve 33 and an one-way valve 34, the other end is connected to a unshowned pump, and this pump flows in this supply pipeline 32 this working medium.
What be suitable as working medium for example is a lubricant oil or an engine oil, and for example this oil is the lubricating oil system of taking from this large-scale diesel engine 1.Working medium in this first fluid system 30 can be identical material with hydraulic medium in this second fluid system 40, for example takes from this large-scale diesel engine 1 lubricant oil supply system and is used for both oil of fluid system 30,40.Yet,, therefore introduce the oil content that the oil ratio of this second fluid system 40 introduces in the first fluid system 30 and do not carry out meticulousr filtration or purification because this second fluid system 40 comprises each component more responsive to impurity.Also very natural is: can use a kind of material different with the hydraulic medium in this second fluid system 40 as the working medium in this first fluid system 30.
This outlet valve 20 comprises a valve body 21, and this valve body is opened or closed with the firing chamber of this cylinder 2 with the connection that this firing chamber is connected between the gas exhaust piping on this vent systems according to its position.In addition, this outlet valve 20 comprises a driven plunger 22 that drives this valve body 21.This valve body 21 remains in closed position shown in Figure 1 by a pneumatic spring 23.Above this driven plunger 22, in the drawings, this pressure piping 31 is opened in this outlet valve 20, so the end face of this driven plunger 22 can be exerted pressure by operation medium.
The electric controller that is used to control this large-scale diesel engine for example comprises that one is carried out the center cell 90 of whole control and the control module of at every turn each cylinder being controlled 91 to this large-scale diesel engine, controls the cylinder of concrete function by means of this control card.The control module 91 of each single cylinder is connected on this center cell 90 by data/address bus.This center cell 90 is also connected on the shaft encoder that does not illustrate in addition, can determine the rotational speed of bent axle 3, each position of crankshaft rotating angle and piston by means of this encoder.For safety, be provided with two automatic shaft encoders.This shaft encoder is connected on this bent axle 3 with being driven.Concerning each shaft encoder,, a reference encoder device is set in order to follow the tracks of the lazy-tongs between this bent axle 3 and this shaft encoder.By means of the signal that receives from this shaft encoder and other suitable data, this center cell 90 is determined the instantaneous working state and the ideal operation state of this large-scale diesel engine 1, and the information that requires is passed to each independent control module 91.Consider the instantaneous load and the transient speed of this diesel engine, each control module 91 is determined the best injection time of each cylinder, fuel injection quantity and scavenging air valve, the i.e. driving time of outlet valve 20 point, thereby automatically controlled signal is transported to separately pilot valve place, controls oil spout and ventilation then.Being connected among Fig. 1 between control module 91 and the pilot valve 60 do not illustrate.
The method of work of this air exchange system 10 will be described below, and described explanation is to make with reference to the normal working of this large-scale diesel engine 1.Can suppose that the valve body 21 of outlet valve 20 and the control piston 56 of main control valve 50 are in the closed position shown in Fig. 1 and the 1A in each case, and the isolation piston 72 of dielectric separator 70 is in i.e. in the drawings the contacting point, bottom of initial position one.The pressure piping 31 and the chamber 71 of these isolation piston 72 tops are full of working fluid.
Event exhaust valve is opened for 20 this moments, and then the control module 91 of this cylinder 2 sends a corresponding electrical signal for this pilot valve 60.This pilot valve 60 cuts out and enters position shown in Figure 1 then, and sets up the fluid connection between branch road 43a and pipeline 65, so that hydraulic medium flows out this liquid-storage container 41, flows to the control import 52 of this main control valve 50, and makes this control piston 56 downsides pressurization.Therefore this control piston resists the resilient force of spring element 57, and moving in the top in figure, thereby at first closes this hole, return flow line 55, opens import 51 then.This moment, control piston 56 was in the enable possition.In the enable possition of control piston 56, the space of isolation piston 72 belows is by branch road 43b, and the import 51 and second connecting passage 54 are connected on this liquid-storage container 41, thereby this hydraulic medium is full of the downside and the pressurization of this isolation piston 72 shown in the figure.Even now, isolation piston still moves upward.This driven plunger 22 that passes to this outlet valve as the working medium in the pressure piping 31 of a hydraulic rod that moves through.Because the result of the pressure effect that working medium is set up, the power that this driven plunger 22 makes valve body 21 head on pneumatic spring 23 enters the enable possition.
In order to close outlet valve 20, because of the result of electrical signal effect, this pilot valve 60 switches to the second place, and the fluid of closing in this position between liquid-storage container 41 and the pipeline 65 connects, so the downside of this control piston 56 is not connected on this liquid-storage container 41.The effect of the elastic force by this spring element 57, this control piston 56 moves downward in figure, thereby closes import 51, has so just closed the connection between this liquid-storage container 41 and isolation piston 72 downsides, and opens the return port 55 of this main control valve 50.This moment, this main control valve 50 was in its closed position, but wherein the connection between this first connecting passage 53 and this return port 55 is opened, so hydraulic medium can flow out from the space acting of these isolation piston 72 belows by this first connecting passage 53 and pipeline 47, flows in this return-flow system 49.
Because of the result of pneumatic spring 23 effect of outlet valve 20, driven plunger 22 is forced to top motion among the figure, and working medium is moved in this pressure piping 31.This outlet valve 20 is closed.By moving into the effect of the working medium in this pressure piping 31, the isolation piston 72 of this dielectric separator 70 is forced to below motion in the figure, and the effect that makes hydraulic medium pass through the control piston 56 of this main control valve 50 in movement process moves into this return-flow system 49 from its downside.By the effect of this pneumatic spring 23, this isolation piston 72 almost is pushed gets back to the initial position that defines shown in Fig. 1 and the 1A.Because the continuous gas exchange action (not shown) that is for example undertaken by the air-vent that is arranged in this outlet valve 20, a few thing medium has constantly lost from the pressure piping 31 as hydraulic rod.This ventilation is closed during the opening state of outlet valve 20, preferably closes automatically by the position of driven plunger 22.At the time durations of ventilation next time, replenish again by supply pipeline 32 and one-way valve 34 because of taking a breath and leaking the working medium that loses, so this isolation piston 72 moves to its initial position fully up to this outlet valve 20.
The dielectric separator 70 that has an isolation piston 72 have with have cleaning hydraulic medium second fluid system 40 with have the function that more impurity do not separate in such a way through the first fluid system 30 of the working medium of fine filtering usually, promptly, on the one hand, effective contact of existence activity between this first and second fluid system, on the other hand, can prevent effectively that working fluid from infiltrating through this second fluid system.In normal work period, can guarantee that the below of this isolation piston 72 has the pressure higher than its top, so can not permeating this isolation piston, working medium do not enter this second fluid system.Yet, on the other hand, from this second hydraulic system 40, flow through this isolation piston and might there be leakage in the hydraulic medium that flows in this first fluid system 30.Because lower to the requirement of this first fluid system 30 aspect purification, therefore this leakage can not produce very big influence.
In addition, the motion of the valve body 21 of outlet valve 20 is promptly cushioned by isolation piston 72 towards motion end separately at end position.
In a preferred embodiment, the driven plunger 22 of this scavenging air valve 20 forms a ladder piston.As shown in Figure 1, this driven plunger 22 comprise that a bigger piston 22a and one are removable and be arranged on one heart among this bigger piston 22a than small piston 22b.Like this, the factor of including consideration at first is: open valve body 21 for the pressure of the pressure of the combustion gas of resisting the firing chamber and pneumatic spring 23, when opening this outlet valve 20, necessarily require to have a bigger power.When firing pressure part let out remove after, in order to make this valve body 21 be in full open position or to remain on this position, only need less power to get final product.When outlet valve 20 was opened, this big small piston 22a, 22b at first resisted the together below motion in the figure of the pressure that exists in the cylinder 2.After moving to a Valve travel of being scheduled to, this big piston 22a runs into one by shoulder 24 in the mode of damping, therefore can not further move.And the remaining part of this Valve travel only needs littler power, and 22b finishes by this small piston, and this moment, this small piston continued to move downward and big piston is static.By the design of driven plunger 22 as a step piston, can save the hydraulic pressure energy to a certain extent, for example can save about 30%.
In the large-scale diesel engine 1 that does not have Control Shaft, the correction between the open and close timing points of the position of bent axle 3 and outlet valve no longer forcibly provides.Therefore this outlet valve 20 comprises two sensors, and promptly the path measurements sensor 25, and the sampling of this sensor is surveyed awl 26 and is connected to securely on this valve body 21, so that survey the motion or the position of this valve body 21 respectively.The measurement signal of this path measurements sensor 25 is transferred to this electric controller by unshowned signal line, so this electric controller is known actual some switching time.According to the signal that this sensor 25 is measured, whether this control gear can discern the motion of this scavenging air valve corresponding to ideal value, and takes appropriate measures when breaking down, for example by closing corresponding cylinder by oil spout.For redundancy is provided with two sensors 25.
Therefore, can determine any desirable opening and closing time point of this outlet valve 20 by means of electric controller, because of this pilot valve 60, the hydraulic pressure fluctuation, the pressure surge influence of pneumatic spring 23 and the rubbing action of whole air exchange system 10 are poor issuable lag time, therefore preferably the time point of opening and closing are regulated.
Owing to adopt two fluid system 30 and 40 pairs of these scavenging air valves 20 that separate by dielectric separator 70 to carry out hydraulic driving, therefore might open the cylinder head of cylinder 2, and not need to open this second fluid system 40.Because the additional hydraulic systems of these cylinder 2 usefulness can be by stop valve 33,44,45 effects disconnect with other parts of motor, therefore still may make one to have and reduced working cylinder quantity, and for example the n Cylinder engine of (n-1) individual working cylinder continues operation.Therefore, can place under repair or maintenance in single cylinder, and there is no need to close whole large-scale diesel engine 1.
The further favourable measure that increases this motor safety in operation is that a leaf spring 27 is set in this outlet valve 20, and it can prevent that this valve body 21 or the component that are attached thereto from running into machinery and not braking by shoulder.In embodiment as herein described, this leaf spring 27 is provided with in such a way, promptly firmly is connected to detection core 26 on the valve body 21 and can resists this leaf spring 27 move upward when opening movement.If this outlet valve 20 can not be closed under certain reason fully, driven plunger 22 can not be in closed position shown in Figure 1 so.If at the next open period of outlet valve 20, this isolation piston 72 pushes all working medium in the pressure piping 31, and then this outlet valve 20 or valve body 21 lean against one by takeing on upward and not braking with high-speed motion respectively.Owing to have the kinetic energy effect of the valve body 21 of big quality, will cause serious damage.In order to prevent this from occurring, leaf spring 27 is set.This detection awl 26 moves in this leaf spring, and this leaf spring absorption kinetic energy, therefore valve body 21 is braked.
Because the result of already mentioned continuous ventilation, this pneumatic spring 23 can guarantee that this scavenging air valve 20 closes after the regular hour automatically when this hydraulic system is out of order, and this continuous vent valve for example is arranged between pressure piping 31 and the driven plunger 22.This large-scale diesel engine is in when static, even when this pilot valve 60 is in the position that makes the exhaust valve opening under the normal working, also keeps like this.
An embodiment's as herein described special advantage is as can be seen: the spring element 57 in the main control valve 57 is subjected to towards the partial pressure of the direction of closed position control piston 56, promptly on this control piston 56, apply a power, the direction of this power is such, so that it attempts to make this control piston 56 to move to closed position or remain in closed position.If there is not pressure in the liquid-storage container 41, promptly start before this large-scale diesel engine 1, it can guarantee that this control piston 56 is in the closed position.By this measure, in this liquid-storage container 41 during the build-up pressure, or at this large-scale diesel engine between the starting period, can prevent that these outlet valve 20 of short duration accidents from opening, start air and from cylinder 2, flow out thereby make.
The preferred driving process of this pilot valve 60 is described below with reference to Fig. 4.Valve actuator is provided for that this pilot valve 60 is carried out electricity and drives, this driver for example with this control card 91 make one and by fill with on each electromagnet 67a of current drives, 67b (Fig. 3).If these pilot valve 60 switchings are left enable possition shown in Figure 3 and gone forward side by side into closing the position, then this valve actuator receives a control impuls that comes from this control module 91 at the proper time point place.Because the effect of this control impuls, valve actuator produce an induced field current herein in a coil of corresponding electromagnet (being electromagnet 67b).Fig. 4 represents the plotted curve of this induced field current I as the function of time t.At time t
aThe place, this valve actuator is connected induced field current I, therefore drives this electromagnet 67b.Put t detection time by means of a right sensors
b, at these time point place magnetic slider 62 setting in motions.That does not have the coil of DM 67b can specifically be used as the sensor that begins to detect to the motion of this magnetic slider 62.By the motion of slider 62, promptly in this coil, produce an induced voltage, this voltage just can be detected when the motion beginning, and shows in this valve actuator.After motion began to be detected, this valve actuator was waited for a preset time interval of delta t, then at time point t
cThe place cuts off this induced field current I, so this electromagnet 67b is ineffective.This time lag, Δ t preferably chose like this, so that it is corresponding with the switching time of this pilot valve 60 basically, for example was about 0.5 millisecond.After the induced field current of coil 67b was cut off, magnet valve slider 62 still was in electromagnet 67b place because of the magnetic remanence effect, and is therefore in the closed position, till this pilot valve 60 switches to the enable possition by another electromagnet 67a driving.
Behind these magnet valve slider 62 setting in motions, by measurement,, can the needed electric current of reliable switching that carry out pilot valve be optimized in transit time during interval of delta t to the cut-out of magnetizing current, therefore can prevent the overheated of this pilot valve 60 or infringement.
The maximum duration of electric current in this valve driver element determined by security reason.At time point t
dWhether locating this magnetoelectricity stream finally is (as shown in phantom in Figure 4) of cutting off automatically, be detected irrelevant with the motion of this valve slider 62.Therefore, the maximum time that electric current flows in magnet spool, i.e. (t
d-t
a) can be determined, so even when producing fault, the overheated of pilot valve also can be got rid of.
Therefore the driving process of pilot valve 60 described herein is not restricted to this scavenging air valve pilot valve, but can be applicable to all solenoid pilot valves of internal-combustion engine by the mode of analogy, for example also applicable to the pilot valve of ejecting system and start-up system.
A further optimized Measures is by means of a predetermined pulse this pilot valve 60 to be switched to an assigned position, the closed position of this air exchange system before this position preferably starts corresponding to this large-scale diesel engine 1.Therefore, for example after this engine long time parking, because this pilot valve is a bistable valve, therefore the possibility that exists is that this pilot valve may be in indefinite or unknown position.For fear of when starting, this scavenging air valve 20 produces undesirable driving, and this electric control device flows to this valve driver element with a predetermined pulse, and this valve driver element switches to an assigned position with this pilot valve then, under the situation of air exchange system, this position is closed position preferably.
Claims (11)
1. the air exchange system used of internal-combustion engine, it comprises: one can be by hydraulically powered scavenging air valve (20) and a first fluid system (30) that is used for a working medium, this first fluid system is connected on this scavenging air valve (20), be used to drive this scavenging air valve (20), it is characterized in that: second fluid system (40) that is used for a hydraulic medium, one is arranged on the main control valve (50) that is used to drive this scavenging air valve (20) in this second fluid system (40), and dielectric separator (70) that is arranged between this main control valve (50) and the scavenging air valve (20), one end of this dielectric separator (70) is connected in this first fluid system (30), and the other end is connected on this second fluid system (40).
2. air exchange system according to claim 1, wherein this main control valve (50) comprising: the control piston (56) with an enable possition and a closed position, when this internal-combustion engine normally moves, the enable possition of this piston is opened this scavenging air valve (20), and closed position is closed this scavenging air valve (20).
3. as air exchange system as described in the claim 2, wherein this main control valve (50) comprising: a spring element that is provided with by following mode (57) makes this spring element apply the power towards this closed position direction for this control piston (56).
4. the described air exchange system of arbitrary as described above claim, wherein this solenoid pilot valve (60) is arranged in this second fluid system (40), is used to guide this main control valve (50).
5. the described air exchange system of arbitrary as described above claim, wherein this scavenging air valve (20) has a driven plunger (22) that is used to drive this scavenging air valve (20), described driven plunger (22) form a step piston (22a, 22b).
6. the method for the air exchange system work in the internal-combustion engine, wherein a scavenging air valve (20), be is characterized in that by hydraulic driving by a working medium and by means of a first fluid system (30): be used to drive a main control valve (50) of this scavenging air valve (20) by second fluid system (a 40) driving that is used for hydraulic medium; And form this first and second fluid system (30 by a dielectric separator (70), 40) the effective connection between, this separator (70) is arranged between this main control valve (50) and the scavenging air valve (20), and the one end is connected in this first fluid system (30), and the other end is connected on this second fluid system (40).
7. as method as described in the claim 6, wherein apply towards a power of the closed position of this control piston (56) for a control piston (56) of this main control valve (50) by a spring element (57), when this internal-combustion engine normally moved, described closed position was closed this scavenging air valve (20).
8. as method as described in claim 6 or 7, wherein this main control valve (50) is by a solenoid pilot valve (60) guiding, and this pilot valve (60) has a magnetic slider (62), and this slider can (67a switches between 67b) back and forth at two electromagnet.
9. as method as described in the claim 8, wherein in order to drive this pilot valve (60)
-two electromagnet (67a, one in 67b) is driven,
-detect the beginning of the motion of this magnetic slider (62); And
-from this magnetic slider setting in motion later in case when one preferably over and done with corresponding to the time lag (Δ t) of switching time of this pilot valve in fact, just make this electromagnet lose excitation.
10. as method as described in claim 8 or 9, wherein this pilot valve (60) switches to one preferably corresponding to the assigned position of the closed position of this scavenging air valve (20) by a predetermined pulse before this internal combustion engine start.
11. a large-scale diesel engine that comprises each described air exchange system of claim 1-5, the perhaps large-scale diesel engine that moves with each described method of claim 6-10.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP00810006.7 | 2000-01-06 | ||
| EP00810006 | 2000-01-06 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1302944A true CN1302944A (en) | 2001-07-11 |
| CN1201065C CN1201065C (en) | 2005-05-11 |
Family
ID=8174507
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB011013885A Expired - Fee Related CN1201065C (en) | 2000-01-06 | 2001-01-05 | Air change system of internal combustion engine and operating method of said air change system |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP1114918B1 (en) |
| JP (1) | JP4576054B2 (en) |
| KR (1) | KR100727476B1 (en) |
| CN (1) | CN1201065C (en) |
| DE (1) | DE50007373D1 (en) |
| DK (1) | DK1114918T3 (en) |
| PL (1) | PL199631B1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100406687C (en) * | 2003-06-23 | 2008-07-30 | 玛涅蒂玛瑞利动力系公开有限公司 | Electrohydraulic unit for actuating the valves of an endothermic engine |
| CN103939169A (en) * | 2014-05-05 | 2014-07-23 | 王欣亮 | Electro-hydraulic valve for engine and working system thereof |
| CN103423016B (en) * | 2012-05-14 | 2016-06-01 | 通用汽车环球科技运作有限责任公司 | Comprise the engine of the oil pressure path with ventilation part |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006010841B3 (en) * | 2006-03-09 | 2007-08-09 | Man B&W Diesel A/S | Two hydraulic-operable fuel injection devices e.g. fuel injectors, temporally shifted activation controlling device, has main valve gate brought into middle position by activated centering device with passivated displacement device |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59188016A (en) * | 1983-04-08 | 1984-10-25 | Hitachi Zosen Corp | Hydraulically operated valve control device |
| JPS59229010A (en) * | 1983-06-09 | 1984-12-22 | Mitsubishi Heavy Ind Ltd | Exhaust valve driving device of internal-combustion engine |
| JPS62613A (en) * | 1985-06-27 | 1987-01-06 | Mitsubishi Heavy Ind Ltd | Scavenged gas pressure utilization type tappet mechanism |
| DK0539320T3 (en) | 1991-10-23 | 1995-03-20 | New Sulzer Diesel Ag | Device for hydraulically activating an exhaust valve in a piston combustion engine |
| US5248123A (en) * | 1991-12-11 | 1993-09-28 | North American Philips Corporation | Pilot operated hydraulic valve actuator |
| US5410994A (en) * | 1994-06-27 | 1995-05-02 | Ford Motor Company | Fast start hydraulic system for electrohydraulic valvetrain |
| DE19528792C1 (en) * | 1995-08-04 | 1996-08-14 | Daimler Benz Ag | Brake for diesel engine |
| DK0767295T3 (en) * | 1995-10-03 | 2000-06-05 | Wortsilo Nsd Schweiz Ag | Hydraulic valve drive |
-
2000
- 2000-12-05 DK DK00811149T patent/DK1114918T3/en active
- 2000-12-05 DE DE50007373T patent/DE50007373D1/en not_active Expired - Lifetime
- 2000-12-05 EP EP00811149A patent/EP1114918B1/en not_active Expired - Lifetime
- 2000-12-28 KR KR1020000084391A patent/KR100727476B1/en active IP Right Grant
-
2001
- 2001-01-04 PL PL344952A patent/PL199631B1/en not_active IP Right Cessation
- 2001-01-05 CN CNB011013885A patent/CN1201065C/en not_active Expired - Fee Related
- 2001-01-05 JP JP2001000264A patent/JP4576054B2/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100406687C (en) * | 2003-06-23 | 2008-07-30 | 玛涅蒂玛瑞利动力系公开有限公司 | Electrohydraulic unit for actuating the valves of an endothermic engine |
| CN103423016B (en) * | 2012-05-14 | 2016-06-01 | 通用汽车环球科技运作有限责任公司 | Comprise the engine of the oil pressure path with ventilation part |
| CN103939169A (en) * | 2014-05-05 | 2014-07-23 | 王欣亮 | Electro-hydraulic valve for engine and working system thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1114918A2 (en) | 2001-07-11 |
| JP2001234717A (en) | 2001-08-31 |
| CN1201065C (en) | 2005-05-11 |
| DK1114918T3 (en) | 2004-09-06 |
| JP4576054B2 (en) | 2010-11-04 |
| KR100727476B1 (en) | 2007-06-13 |
| PL199631B1 (en) | 2008-10-31 |
| DE50007373D1 (en) | 2004-09-16 |
| EP1114918A3 (en) | 2002-10-09 |
| EP1114918B1 (en) | 2004-08-11 |
| PL344952A1 (en) | 2001-07-16 |
| KR20010070375A (en) | 2001-07-25 |
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