CN1485530A - Hydraulic control valve - Google Patents
Hydraulic control valve Download PDFInfo
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- CN1485530A CN1485530A CNA031564445A CN03156444A CN1485530A CN 1485530 A CN1485530 A CN 1485530A CN A031564445 A CNA031564445 A CN A031564445A CN 03156444 A CN03156444 A CN 03156444A CN 1485530 A CN1485530 A CN 1485530A
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/08—Shape of cams
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Abstract
To provide a valve operated with hydraulic pressure for an internal combustion engine. The valve operated with hydraulic pressure for the internal combustion engine is equipped with a hydraulic pressure type actuator for operating the valve to the position of seating on and the position of separating from, a primary pressure chamber 35 where the pressurized fluid acts on the surface of a first piston to be an extended position, a port 11 capable of mutually connecting to the high pressure source of the working fluid or a return line, and a first flow path between the port and the primary pressure chamber. It has means 48, 49, 36, 36', 36'', 55 for changing flow resistance of the first flow path in relation to the position of the first piston. The valve has a stem 24 which is operatably connected to the first piston 32 arranged in a fixed housing 31 of the actuator. The first piston is at the retracted position when the valve seats on the seat, and at the extended position when the valve separates from the seat. (C)2004,JPO.
Description
Technical field
The present invention relates to a kind of hydraulic control valve, this hydraulic control valve is applied to internal-combustion engine, for example two-stroke or four-cycle diesel, perhaps gas engine.Described valve can be used as suction valve or outlet valve.Particularly the present invention relates to a kind of hydraulic control valve that is used for internal-combustion engine, this hydraulic control valve is included in the hydraulic actuator that is used to operate described valve between a fixed position and the on-fixed position, above-mentioned valve has a bar portion that is operably connected on the first piston, this piston is positioned at a hole of the set casing of described actuator, therefore, when described valve is fixed, above-mentioned first piston is positioned at the place, retracted position, and when described valve is not fixed, above-mentioned first piston is positioned at extended position, one main pressure chamber, pressurized fluid acts in this pressure chamber on the surface of described first piston to drive it to described extended position, one aperture, described aperture can be connected to the high-voltage power supply place of a hydraulic fluid, or being connected to a return line place and a primary flow path alternatively, this primary flow path is between described aperture and described main pressure chamber.
Background technique
This valve acutator is operated by high pressure hydraulic fluid, and by a switch type valve, described high pressure hydraulic fluid is supplied to described hydraulic actuator from a special-purpose common rail system.For overcome in the firing chamber back pressure and for the motion of described valve is quickened, a high relatively pressure need be provided, described back pressure acted on the described valve in the phase I of opening movement.But when described valve was opened slightly, the back pressure in the firing chamber can reduce significantly.Owing in the overwhelming majority of whole stroke, all need to apply hydraulic pressure, so described actuator and described valve can be with the end of quite high speed towards stroke.Under the situation of the end that does not have stroke damper, described piston can be with totally unfavorable high-speed impact to stroke limiter, and this will cause its damage and noise.
U. S. Patent the 3rd, 209, disclosed a kind of hydraulic actuating outlet valve for No. 737, in described hydraulic actuating outlet valve, actuator piston is positioned at two parts, wherein large diameter first piston part is round one second piston portion, and described second piston portion is made into a complete part of the bar portion of described valve.Described second piston portion has a vertical pin that upwards is passed in the dampening chamber, forms a hydraulic bjuffer with the tail end at described hydraulic driving closing motion, therefore slows down the closing motion of described valve.One similar equipment is provided in the tail end of described unlatching stroke.
Hydraulic damper is with following principle work, and promptly described hydraulic fluid is limited in the Room, and can only discharge by the matching gap between the hole of the part of the piston that enters into described dampening chamber and described chamber.On its stroke limiter, the impact on any bearing that occurs in described piston can both relax by the size of selecting described slit suitably.Therefore, a restriction, promptly described hydraulic damper can only be at described piston with a specific speed near well operation under the situation of described damper, just, by selecting suitable matching gap, they can be calibrated.Owing in described common rail system, have the variation of pressure, so when the speed at the described damper of described piston arrives place changed, described damper can not suitably be worked.
But sizable variation can take place in the pressure of the high-pressure liquid that is produced by internal-combustion engine.Owing to there is not enough kinetic energy fully to enter into described dampening chamber to force described piston, the pressure that institute's ether is low will cause described valve fully not opened, and because absorbed too many kinetic energy by described hydraulic damper in described piston, the pressure that institute's ether is high can cause that again described piston strikes on the described stroke limiter too fiercely.The variation of described hydraulic fluid viscosity will aggravate this problem.
Summary of the invention
Under this background, the purpose of this invention is to provide a kind of hydraulic control valve of mentioning at first, this hydraulic control valve has overcome above-mentioned problem, and can work in the supply pressure scope of a broad, for example typically is present in to be used for fuel-injected rail altogether.According to claim 1, can realize this purpose by the hydraulic control valve that a kind of the above-mentioned type is provided, above-mentioned hydraulic control valve comprises that also the position with respect to described first piston is used to change the device of the flow resistance of above-mentioned primary flow path.
Therefore, the hydrodynamic pressure in the main pressure chamber can reach expected value along the stroke of described valve.So described piston activated with a high relatively pressure in the beginning of opening stroke, to overcome the back pressure in the firing chamber and to make valve accelerated motion, and the remainder at described unlatching stroke moves to avoid described valve to reach too high speed with a low relatively pressure, therefore it can gently be rested on the stroke limiter.So the variation in pressure that is fed to the hydraulic fluid in the actuator is very little to the dynamic characteristic influence of described valve acutator.Therefore, it is possible utilizing the high-pressure liquid (fuel) that for example derives from the common rail system that is used for the fuel injection, and as the source of the high pressure hydraulic fluid that is used for described valve acutator, according to the running state of motor, described high pressure hydraulic fluid is to change.So, can under the situation of the special high-pressure common rail system that is not used in described valve acutator, construct motor.
Preferably, the device that can be provided for making the flow resistance of primary flow path to change is so change according to the predetermined described flow resistance of profile with respect to the position of described first piston.Depend on the design of described valve and desired opening profile, perhaps according to any other desired profile, described flow resistance can progressively linearly progressively increase.
So far, described first piston comprises a tapering part, and inwardly outstanding flange has formed the restriction of flowing together in the hole of this tapering part and from described actuator housings, when described first piston when the retracted position moves to extended position, above-mentioned flow restriction increases, and vice versa.
Described tapering part is the shape of a truncated cone haply, to obtain a linear circulation area that reduces.In order to have an outside a little curvilinear surface, the described truncated cone can be modified, to form an inside a little curvilinear surface of connection area or that reduces fast, so when described first piston moved to described extended position, the described truncated cone was funnel-like to be used to gradually reduce the connection area.
In another preferred embodiment, described primary flow path comprises a plurality of smaller pipelines, when described piston when described retracted position moves to described extended position, above-mentioned pipeline is opened by piston one by one at place, described retracted position, and closed one by one by piston in described extended position, vice versa.Therefore, when described first piston when the retracted position moves to extended position, the flow restriction in the primary flow path increases.Depend on desired profile, described pipeline can have identical flow resistance or different flow resistances.
Alternatively, described actuator housings can have an angled orifices, this angled orifices is led to indoor in the described actuator housings, and described angled orifices and described first piston interact and form a flow resistance, and this flow resistance can change with respect to the position of described first piston.Therefore, described flow restriction can the continually varying mode change.
Described valve acutator also comprises:
One second piston, this second piston and the coaxial setting of above-mentioned first piston, and act on the above-mentioned first piston phase I with the stroke of the first piston that is implemented in described extended position place,
One secondary pressure chamber, wherein pressurized fluid acts on the surface of described second piston driving it at described extended position place,
One secondary stream, this secondary stream are between above-mentioned aperture and above-mentioned secondary pressure chamber and be used to close the device of above-mentioned secondary stream before the end of described its working stroke of second piston arrives.Assist described main piston to overcome back pressure at second piston described in the firing chamber.Closing described secondary stream in time helps avoid described second piston and impinges upon too fiercely on its stroke limiter.
On the fixed speed of described valve and the described stroke limiter first piston in abutting connection with speed also can be by being used for described main piston the end of stroke damper of the shape that is blind dampening chamber reduce, in the tail end of corresponding stroke, the part of described first piston is trapped in the described blind dampening chamber.
According to the present invention, the more purpose of described hydraulic control valve, feature, advantage and characteristic will become clearer by the description of following embodiment.
Description of drawings
In the concrete enforcement part of the present invention below, will present invention is described with more details by middle illustrated embodiment with reference to the accompanying drawings, wherein:
Fig. 1 is the sectional view of cylinder profile in having the two-stroke cross head h type engine h of cylinder head;
Fig. 2 is first embodiment's the longitdinal cross-section diagram that has the hydraulic actuating outlet valve of valve seat in the cylinder shown in Figure 1 and be positioned at the described first piston at its place, retracted position;
Fig. 3 is the enlarged cross-sectional view with actuator of the first piston that is positioned at a part of extended position;
Fig. 4 is the identical view as shown in Figure 3 that first piston arrives the stroke limiter place;
Fig. 5 is the opening figure of outlet valve under different hydraulic pressure supply pressure;
Fig. 6 is the viewgraph of cross-section of actuator among second embodiment; With
Fig. 7 is the viewgraph of cross-section of actuator among the 3rd embodiment.
Embodiment
Figure 1 shows that single current, and have the cylinder 1 of the scavenge port 2 that is arranged in bellows 3, described scavenge port 2 comes from not shown ventilation container, and this ventilation container is by for example, and worm wheel pressure booster is provided with the waste gas that pressurizes.
One outlet valve 4 medially is installed in the top of the cylinder in the cylinder head 24 '.End at expansion stroke, described outlet valve was in opening state before engine piston 5 is downwards by described scavenge port 2, therefore the combustion gas in the firing chamber 6 on described piston top are discharged by an exhaust passage 7, and described exhaust passage 7 is outwards led in the degassing container 8.When described piston moved up with an adjustable momentum, described outlet valve was closed once more, and for example, this adjustable momentum depends at the required effective compression ratio with after-combustion.Described outlet valve is upwards driven by air cushion spring 23 in mobile closing.
Consider the serviceability of described valve and consider in the firing chamber favourable, accurate control condition, and the efficient of considering motor thus, preferably, described outlet valve should very accurately be controlled.
Described outlet valve is opened by hydraulic driving actuator 9.By pressure piping 10 supplying hydraulic fluids, described pressure piping 10 is connected to the aperture 11 (only at Fig. 3,4,6, shown in 7) that is positioned on the actuator with control mouthful and locates, and described control mouth is positioned on the upper surface of the switchboard 12 that is supported by a control panel 13.Described control panel is connected on the high pressure pipe line 14, and this high pressure pipe line 14 is used under a pressure from rail (not shown) supplying hydraulic fluid altogether, and this pressure for example can cling in the scopes of 500 crust from 16.Preferably, described rail altogether also can be used as the source of the high-pressure liquid that is used for fuel injection system.
At fuel in this case, be arranged in the described hydraulic fluid of rail altogether and can be used to directly drive described valve acutator, perhaps drive described valve acutator by pressure amplifier/separator indirectly, described separator can separate the hydraulic fluid that is used for valve acutator from the fuel that is arranged in common rail.Pressure in the described common rail fuel system relies on the running state of motor, for example operating rate and load condition and change.Typically, the pressure that is used for the described common rail fuel system of large two-stroke diesel engine can cling to variation between 2000 crust 800.
Be total to rail if be used for the special use of described valve acutator, can from storage tank, pass through the pumping plant supplying hydraulic fluid so, described hydraulic fluid, for example a kind of standard hydraulic oil, but preferably, can be with the lubricant oil in the motor as hydraulic fluid, and give described system supply from the oil groove of motor.
But described internal-combustion engine middling speed four-cycle diesel or gas engine, or low speed two-stroke cross head diesel engine, its a kind of propelling motor or a kind of fixing prime mover that is used for the power station that is used for boats and ships.
Each cylinder of motor all links to each other with a control electronics 15, this control electronics 15 by lead 16 receive total synchronously and control signal, and in other parts, automatically controlled signal is sent to a control valve 17 places by lead 18.Can be that each cylinder all has a control apparatus 15, or several cylinder be continuous with identical control apparatus.Described control apparatus can also be from a total control apparatus received signal, and this control apparatus is public to all cylinders.
In described control panel, the passage of pitching out from the punishment of described high pressure pipe line 19 is sent to a high-pressure orifice on the described control valve 17 with the supporting roll hydraulic fluid.
Described passage 19 has a plurality of fluid collectors 20, when described control valve is opened, and when described control valve is closed from described high pressure pipe line by after supply with in, this fluid collector 20 can be carried most flows.
Control mouth on the described control valve 17 is connected to exhaust port place on the upper surface that is positioned at described switchboard 12 by the passage 21 in the described switchboard.Described control valve also has one jar of mouth, and this jar mouth is connected to a reflow pipe place that is used to transmit the hydraulic fluid of using by the return line 22 of a passage shape.Alternatively, described return line 22 can under atmospheric pressure be connected to a waste pipe place, and for example, one leads to the waste pipe of engine oil sump.The excursion of the pressure in the described return line can be pressed onto the overvoltage of several crust from atmosphere.Penetrate into described actuator for fear of air, described return line 22 preferably has an overvoltage, and for example overvoltage of at least 1 crust is so when described hydraulic fluid is discharged from, can keep this overvoltage in pressure piping 10 from described actuator.
When described outlet valve 4 when being unlocked, the control signal that comes from described control apparatus 15 drives described control valve 17 to one positions, be connected on the described control mouth at the described high-pressure orifice 19 in this position, enter the mouth described pressure piping 10 places freely and therefore arrive described fluid supply port 11 places again so that high-pressure liquid has.When described outlet valve 4 when being closed, described control valve 17 is driven to a position, the described jar mouth that is connected on the return line 22 is connected to described control and mouthful locates in this position, so the high pressure in the pressure piping 10 is discharged from.
Described control valve 17 is the type of any routine, for example two-bit triplet unidirectional electrical driving switch valve.But, in order to obtain fast, accurate activated valve device, shown in control valve 17 preferably form by two-part, that is, a mortor operated valve 17a and is used for the main valve 17b of described valve acutator.But described mortor operated valve 17a two-bit triplet.For example, it has the type of magnetic padlock in extreme position, driven in the magnetization of the described valve in this position by a coil in two coils, and described two coils are positioned on the end of a valve slider separately, and this valve slider is made by ferromagnetic substance.The safety measure that lost efficacy as the magnetization that prevents described two coils, but the described valve slider of a spring precompressed in this position, is main supply ports to the jar mouth of described return line 22 to an inoperative position of supposition.Alternatively, the described mortor operated valve solenoid valve of a routine.The exhaust port of described mortor operated valve is connected to a center-aisle place, this center-aisle is communicated with the piston face place of pressure to slider one end of main valve 17b, has a piston face than small size that is connected with described high pressure pipe line enduringly on the other end of described slider.A position at described mortor operated valve, high pressure on the described less piston area is pressed onto a position with main slider, be connected to the exhaust port place of described main valve at the described reflow pipe in this position by described return line 22, described exhaust port leads to pressure piping 10.Be driven to its second place place as described mortor operated valve 17a, when stating center-aisle in this second place place and being connected on the high pressure pipe line 14, the slider of described main valve is pressed onto its second place place than the lip-deep high pressure of big piston, be passed to pressure piping 10 places at the described high pressure in this position, so described actuator is with described exhaust valve opening.
With reference to figure 2-4, will first embodiment of actuator 9 and air cushion spring be described in detail now.
Described outlet valve has one from the upright bar portion 24 of valve disc, and the upper end portion of described bar portion supports a spring piston 25, and this spring piston 25 is fixedly mounted in the described bar portion so that realize wiper seal and vertically replace in pneumatic cylinder 26.Below described spring piston, a spring housing 27 that is connected to superheated steam activity (not shown) is arranged, at a predetermined pressure minimum, the excessive rollings of 4.5 crust for example, described superheated steam activity can make and be full of superheated steam in the described spring housing.Other air pressure also can be used, and for example clings to the pressure of the scope of 10 crust from 3.According to the spring characteristic of desired air cushion spring, described pressure minimum can be selected.It is possible that spring housing on several different cylinders is connected with each other, and still, preferably, can not return valve 56 by one independently in each spring housing of described superheated steam activity and closes.Superheated steam in the described spring housing 27 produces one and continues power upwards on described spring piston 25.When described spring piston 25 to bottom offset and when compressing gas in the described spring housing 27, should power upwards just increase, prevent the overflowing of gas in the spring housing 27 by the described valve that do not return.
One shell 28 is around described air cushion spring and produce a cavity 29 thereon.Described cavity is connected to a waste pipe 57 places, so described cavity has barometric pressure.
Described hydraulic actuator 9 constitutes from cylinder 31, and this cylinder is by the upper support of described shell 28.One first piston 32 is accommodated in the center hole of described cylinder 31.Described center hole is closed at the place, top of described cylinder, and opens at the place, bottom of described cylinder 31.Described center hole and one is arranged in the hole 34 coaxial settings of described shell 28.
One main pressure chamber 35 is defined between the top of cylinder 31 and described first piston.Hydraulic fluid is fed into and discharges described valve acutator by an aperture 11.Aperture 11 is connected to 36 places, aperture by a pipeline 30, and the described center hole in the cylinder 31 is led in this aperture 36.Alternatively, aperture 11 links to each other with described high-voltage power supply, or links to each other with described return line.An intermediate pressure chamber 37 is led in described aperture 36, and this intermediate pressure chamber 37 is defined between the part 38 of diameter reduction of described cylinder 31 and described first piston.One pipeline 39 is from pipeline 30 punishment fork, and leads to described center hole with aperture 43 wherein, during the phase I of described unlatching stroke, and the recess 41 in the described aperture 43 of this central hole in the first piston.By described recess 41, described hydraulic fluid arrives in the secondary pressure chamber 40.Described secondary pressure chamber is defined between the part that a diameter of one second piston 42 and described center hole increases, and described second piston 42 is coaxial setting with described first piston.Described second piston is being meshed with the auxiliary latter in the phase I of described unlatching stroke with a flange 45 on the described first piston.The stroke of described second piston 42 is shorter than the stroke of described main piston 32 significantly.At the end of the stroke of described second piston, it contacts with one-stroke limiter 46.Therefore, in the phase I of described unlatching stroke, described first piston and described second piston move together.Because the recess 41 at described first piston place has moved past the position of the described center hole that leads in aperture 43, so touch before its stroke limiter 46 at described second piston, the stream between described secondary pressure chamber 40 and aperture 43 has been closed.Therefore contacted before described stroke limiter at described second piston, the supply of supporting roll hydraulic fluid is through with well, so described second piston gently drops on its stroke limiter 46.
In order to allow described secondary pressure chamber to be drained for closing motion, a reflow pipe 47 with safety check 44 is connected to described secondary pressure chamber on the pipeline 10.
When described outlet valve will be unlocked, described control valve 17 was fed to 11 places, described aperture with described high-pressure liquid, and described first, centre and secondary pressure chamber pressurized all.High pressure hydraulic fluid in described main pressure chamber and the secondary pressure chamber causes described first piston and the simultaneously downward pressurized of described second piston.
The top of described first piston comprises a tapering part 48, and this tapering part 48 top towards described first piston on diameter increases.This tapering part is as shown in Fig. 1-3, and it has an outside a little curvilinear surface, but other surface, a truncated cone for example, an inside a little curvilinear surface, their combination or any desired predetermined profile all are possible.A kind of like this profile is by test, and computer simulation or analytical method determine, what these means were used for showing the optimal dynamic characteristic that is used for described valve acutator will have much along the flow resistance of described stroke in each position.Then, described in view of the above conical surface is configured.
One inwardly outstanding annular flange flange 49 is from described central hole, promptly just in time described aperture 36 lead to described center hole the position above locate to extend.Described tapering part 48 forms a narrow annulus with a size with described annular flange flange 49, and this size changes along with the position of described first piston.Described hydraulic fluid is had to by this slit pressurized to flow to the described main pressure chamber from described intermediate pressure chamber.This causes the pressure drop between described intermediate pressure chamber and the main pressure chamber.When the size of described annulus reduced, this pressure drop just increased, and along with the increase of flow, this pressure drop also progressively increases, so this has prevented that effectively described first piston from reaching too high speed.Described tapering part can be defined size so that described slit diminishes towards the end of described unlatching stroke.So described first piston has been limited effectively towards the speed of the end of described stroke, even the supply pressure of described hydraulic fluid is relatively higher.Described first piston also has an end that is the stroke damper of dampening chamber's 50 shapes.Described flange 45 be defined size with blind dampening chamber in a small gap fit, and when described flange is absorbed in the described dampening chamber, by forcing hydraulic fluid to flow out the mode of described dampening chamber by described small gap, most remaining kinetic energy have been absorbed, and the lower surface of described first piston gently contacts on described stroke limiter 51.
Under the influence of described air spring, described first piston is returned to place, described retracted position.Described actuator also has the end of the stroke damper that is dampening chamber's 52 shapes that is used for described closing motion.The top of described piston be defined size with blind dampening chamber 52 in a small gap fit.When the top of described first piston was absorbed in the described dampening chamber, most remaining kinetic energy had been absorbed, and described valve gently contacts on described valve seat.
The flow resistance of the stream between described aperture 36 and described main pressure chamber 35 can be regulated by the design that changes described tapering part, changes the design of above-mentioned tapering part according to required pressure in the main pressure chamber 35 of the position separately of described first piston.Therefore, described valve acutator can suitably be operated with a high-voltage power supply, and this high-voltage power supply has a variable pressure.Relatively low supply pressure will cause the lower acceleration of described valve.Therefore, it is longer a little that described control electronics 15 can keep the time of described opening of valves.Fig. 5 illustrates described control electronics 15 well and adjusts time limit of described valve opening and the length variation in pressure in supplying with the compensation high pressure hydraulic fluid constantly.Solid line among Fig. 5 is depicted as the time limit of the conventional valve that is used for the titer hydraulic fluid pressure.When described supply pressure is low relatively, described control electronics will be indicated described opening of valves ground relatively earlier, and the time that is held open state is longer relatively, to guarantee being used for the suitably time long enough of the opening of valves of discharge (having shown in the length dotted line at interval) of gas in the firing chamber as Fig. 5, when described supply pressure was higher relatively, vice versa (shown in another dotted line among Fig. 5).
Cylinder comprises that one discharges and reflux line 53, and this pipeline is connected to 34 places, described aperture with main pressure chamber 35.When described first piston was positioned at place, a neutral position, the hydraulic fluid of temperature can be recycled by described actuator.The advantage of this design be when motor not in running state following time, still can keep described valve on operating temperature, and this design also has effective scavenging action.
Figure 6 shows that second embodiment of described valve acutator.Described valve acutator is an identical construction according to first embodiment's valve acutator substantially, except changing the device of the flow restriction of the primary flow path between aperture 11 and the main pressure chamber 35.In the present embodiment, aperture 36 has been replaced by an angled orifices 36 '.Described angled orifices forms a mobile restriction with described top, when described first piston when described retracted position moves to described extended position, this flow restriction just increases, and before the end that arrives described unlatching stroke, described primary flow path has fully been blocked, to prevent that any hydraulic fluid from flowing in the described main pressure chamber further, so described first piston and described valve will slow down in the final stage of described unlatching stroke.Described hydraulic fluid flows in the described intermediate pressure chamber from aperture 36 ' by a pipeline 54, and further flows in the main pressure chamber, and this pipeline 54 is connected to intermediate pressure chamber in the main pressure chamber 35.
Figure 7 shows that the 3rd embodiment of described valve acutator.Described valve acutator is an identical construction according to second embodiment's valve acutator substantially, except changing the device of the flow restriction of the primary flow path between aperture 11 and the main pressure chamber 35.Pipeline 30 is connected to a plurality of narrow relatively pipelines 55 places, below 55 1 in this narrow pipeline is positioned at one by aperture 36 " lead to described intermediate pressure chamber.Flow restriction in the described throat produces a sizable pressure drop at the high flow rate place of described hydraulic fluid.In described unlatching stroke, described aperture 36 is closed on the top of described first piston one by one ".Therefore in described unlatching stroke, the flow restriction in the primary flow path increases step by step.When along the direction of described unlatching stroke, the cross-section area of the narrow pipeline 55 shown in Fig. 7 is along with each narrow passage diminishes.When described first piston moved to described extended position, this had caused the progressively increase of flow restriction in the primary flow path.Alternatively, described pipeline 55 is cross-section area identical (not shown), perhaps has big relatively cross-section area, and a flow limiter (not shown) is set in described pipeline 55.
Pei Zhi air spring can be replaced by a return stroke pressure chamber and a piston face in the above-described embodiments, and this piston face forces described first piston to place, described retracted position.This embodiment (not shown) will need control valve is carried out revising a little, and this control valve can be fed to the supporting roll hydraulic fluid return stroke pressure chamber that is used for described piston is forced to place, described retracted position.As described above, identical principle can be used to control with respect to the pressure in the return stroke pressure chamber of the position of described first piston.
Although at length described purpose of the present invention, be understandable that these details are only used for above-mentioned purpose, and those skilled in the art can make amendment to it in the scope that does not depart from claim with way of illustration.
Claims (9)
1. hydraulic control valve that is used for internal-combustion engine, described hydraulic control valve comprises:
One hydraulic actuator, described hydraulic actuator is used to operate described valve between a fixed position and an on-fixed position, above-mentioned valve has a bar portion (24) that is operably connected on the first piston (32), described first piston (32) is set in the set casing (31) of described actuator, thus, and when described valve is fixed, above-mentioned first piston is positioned at place, a retracted position, and in an extended position, described valve is not fixed
One main pressure chamber (35), wherein pressurized fluid acts on the surface of described first piston it being driven into described extended position,
One aperture (11), alternatively, described aperture (11) can be connected to a high-voltage power supply place of hydraulic fluid, perhaps be connected to a return line place and
One primary flow path, this primary flow path between above-mentioned aperture and above-mentioned main pressure chamber,
It is characterized in that: comprise the device (48,49,36,36 ', 36 ", 55) of flow resistance that is used to change above-mentioned primary flow path with respect to the position of described first piston.
2. hydraulic control valve as claimed in claim 1 is characterized in that: when described first piston (32) when described retracted position moves to described extended position, the flow resistance of above-mentioned primary flow path increases, vice versa.
3. hydraulic control valve as claimed in claim 2, it is characterized in that: above-mentioned first piston (32) comprises a tapering part (48), this tapering part (48) and one inwardly outstanding flange (49) from above-mentioned shell has formed a mobile restriction together, when described first piston when described retracted position moves to described extended position, above-mentioned flow restriction just increases, and vice versa.
4. hydraulic control valve as claimed in claim 3 is characterized in that: the shape of above-mentioned tapering part (48) is the shape of a truncated cone haply, a taper tubular, a funnel-like or their combined shaped.
5. hydraulic control valve as claimed in claim 3, it is characterized in that: above-mentioned tapering part (48) forms a narrow slit along a profile, described narrow slit is positioned between above-mentioned tapering part and the described flange (49), the position of depending on described first piston, this narrow slit changes dimensionally.
6. hydraulic control valve as claimed in claim 2, it is characterized in that: above-mentioned primary flow path comprises a plurality of pipelines (55), when described first piston (32) when described retracted position moves to described extended position, above-mentioned pipeline (55) is opened by described first piston (32) one by one at place, described retracted position, and closed one by one by described first piston (32) in described extended position, vice versa.
7. hydraulic control valve as claimed in claim 2, it is characterized in that: described actuator housings (31) has an angled orifices (36 '), described angled orifices (36 ') is led to an intermediate pressure chamber (37), work to form a mobile restriction with described first piston (32) in above-mentioned aperture (36 '), with respect to the position of described first piston, this flow restriction changes.
8. as each the described hydraulic control valve among the claim 1-6, it is characterized in that: comprise one second piston (42), described second piston (42) and the above-mentioned coaxial setting of first piston (32), and act on the above-mentioned first piston phase I with the stroke of the described first piston on the direction that is implemented in unlatching
One secondary pressure chamber (40), wherein pressurized fluid acts on the surface of described second piston driving it on described opening direction,
One secondary stream, this secondary stream are positioned between above-mentioned aperture (11) and the above-mentioned secondary pressure chamber,
It is characterized in that being included in the device (41) that is used to close above-mentioned secondary stream before the end of described its working stroke of second piston arrives.
9. as each the described hydraulic control valve among the claim 1-7, it is characterized in that: comprise being used for blind dampening chamber (50 of being of described first piston (32), the end of the stroke dampening chamber of shape 52), wherein in the tail end of corresponding stroke, the part of described first piston is trapped in the described blind dampening chamber.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DKPA200201263 | 2002-08-28 | ||
| DKPA200201263 | 2002-08-28 |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA200510008608XA Division CN1651725A (en) | 2002-08-28 | 2003-08-28 | Cross head type large two stroke diesel engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1485530A true CN1485530A (en) | 2004-03-31 |
| CN1314884C CN1314884C (en) | 2007-05-09 |
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Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB031564445A Expired - Fee Related CN1314884C (en) | 2002-08-28 | 2003-08-28 | Hydraulic control valve |
| CNA200510008608XA Pending CN1651725A (en) | 2002-08-28 | 2003-08-28 | Cross head type large two stroke diesel engine |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA200510008608XA Pending CN1651725A (en) | 2002-08-28 | 2003-08-28 | Cross head type large two stroke diesel engine |
Country Status (3)
| Country | Link |
|---|---|
| JP (3) | JP2004084670A (en) |
| KR (3) | KR100538679B1 (en) |
| CN (2) | CN1314884C (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101482041B (en) * | 2005-02-02 | 2011-05-18 | 曼柴油机和涡轮公司,德国曼柴油机和涡轮欧洲股份公司的联营公司 | Crosshead type large two-stroke diesel engine |
| CN101509402B (en) * | 2008-02-14 | 2012-09-05 | 曼柴油机和涡轮公司,德国曼柴油机和涡轮欧洲股份公司的联营公司 | Exhaust valve actuator for large-scale two-stroke diesel engine |
| CN103228878A (en) * | 2010-11-30 | 2013-07-31 | 瓦锡兰芬兰有限公司 | An arrangement and a method of operating a gas exchange valve of an internal combustion engine, a cylinder head and a method of upgrading an internal combustion engine |
Families Citing this family (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2006074497A2 (en) * | 2005-01-17 | 2006-07-20 | Avl List Gmbh | Method for operating an internal combustion engine |
| AT501335B1 (en) * | 2005-01-19 | 2007-05-15 | Avl List Gmbh | Method for operating internal combustion engine, involves locating brake valve on each cylinder, and opening brake valve into common pressure container during engine operation before start or during compression phase of cylinder |
| KR100655038B1 (en) * | 2005-11-11 | 2006-12-06 | 현대중공업 주식회사 | Diesel combustion system driven by rotating cam and flow control valve |
| JP2008248838A (en) | 2007-03-30 | 2008-10-16 | Man Diesel As | Cam driven exhaust valve operation system for large size two cycle diesel engine |
| EP2063075A1 (en) * | 2007-11-23 | 2009-05-27 | EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt | Fluid actuated valve mechanism |
| JP4953250B2 (en) * | 2007-12-20 | 2012-06-13 | 社団法人日本舶用工業会 | Intake / exhaust valve drive system |
| CN102066703B (en) * | 2008-06-25 | 2013-02-13 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | Hydraulic supply system of a large two-stroke diesel engine |
| CN102112708B (en) * | 2008-07-14 | 2014-06-18 | 曼柴油机欧洲股份公司曼柴油机德国分公司 | Cam driven exhaust valve actuation system for large two stroke diesel engine |
| JP5127747B2 (en) * | 2009-03-09 | 2013-01-23 | 三井造船株式会社 | Electronically controlled valve drive device for internal combustion engine |
| DK177283B1 (en) | 2010-02-24 | 2012-10-08 | Man Diesel & Turbo Deutschland | Valve arrangement |
| DK177410B1 (en) | 2010-02-24 | 2013-04-02 | Man Diesel & Turbo Deutschland | Valve actuation system for a large two stroke diesel engine |
| US20120272932A1 (en) * | 2011-04-27 | 2012-11-01 | GM Global Technology Operations LLC | Fluid pressure control valve |
| FI20125250L (en) * | 2012-03-09 | 2013-09-10 | Waertsilae Finland Oy | Gas exchange valve arrangement and gas exchange valve |
| FI124349B (en) * | 2012-03-09 | 2014-07-15 | Wärtsilä Finland Oy | Hydraulic actuator and throttle valve arrangement |
| JP5815584B2 (en) * | 2012-04-10 | 2015-11-17 | エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド | Balance position valve spindle |
| DK177695B1 (en) * | 2012-11-16 | 2014-03-17 | Man Diesel & Turbo Deutschland | A large slow running turbocharged two-stoke uniflow internal combustion engine with crosshead and a cam driven exhaust valve actuation system |
| DK177676B1 (en) * | 2013-02-08 | 2014-02-17 | Man Diesel & Turbo Deutschland | Exhaust valve arrangement for a large slow-running two-stroke internal combustion engine with crossheads |
| CN107676144B (en) * | 2017-09-30 | 2019-12-27 | 中国北方发动机研究所(天津) | Hydraulic variable valve mechanism for 2/4 stroke engine |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59170414A (en) * | 1983-03-18 | 1984-09-26 | Nissan Motor Co Ltd | Hydraulic type valve drive device |
| JPS60249778A (en) * | 1984-05-25 | 1985-12-10 | Yanmar Diesel Engine Co Ltd | Operating piston buffer mechanism of hydraulic valve device |
| JPH0219808U (en) * | 1988-07-23 | 1990-02-09 | ||
| JPH0749011A (en) * | 1993-08-05 | 1995-02-21 | Nippon Soken Inc | Hydraulic valve opening/closing mechanism |
| DK0767295T3 (en) * | 1995-10-03 | 2000-06-05 | Wortsilo Nsd Schweiz Ag | Hydraulic valve drive |
| DK174031B1 (en) * | 1997-05-29 | 2002-04-29 | Man B & W Diesel As | Hydraulically actuated exhaust valve for an internal combustion engine |
| AT410696B (en) * | 1999-09-22 | 2003-06-25 | Jenbacher Ag | VALVE DRIVE FOR A VALVE OF A COMBUSTION ENGINE |
| DK176152B1 (en) * | 2000-07-10 | 2006-10-16 | Man B & W Diesel As | Method of activating an exhaust valve for an internal combustion engine and such an exhaust valve |
-
2003
- 2003-08-27 JP JP2003302427A patent/JP2004084670A/en active Pending
- 2003-08-28 KR KR10-2003-0059960A patent/KR100538679B1/en active IP Right Grant
- 2003-08-28 CN CNB031564445A patent/CN1314884C/en not_active Expired - Fee Related
- 2003-08-28 CN CNA200510008608XA patent/CN1651725A/en active Pending
-
2005
- 2005-03-03 KR KR1020050017736A patent/KR20050033575A/en active Search and Examination
- 2005-04-12 JP JP2005115146A patent/JP2005256843A/en active Pending
- 2005-09-21 KR KR1020050087744A patent/KR20050099602A/en not_active Application Discontinuation
-
2008
- 2008-02-20 JP JP2008038805A patent/JP4657311B2/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101482041B (en) * | 2005-02-02 | 2011-05-18 | 曼柴油机和涡轮公司,德国曼柴油机和涡轮欧洲股份公司的联营公司 | Crosshead type large two-stroke diesel engine |
| CN101509402B (en) * | 2008-02-14 | 2012-09-05 | 曼柴油机和涡轮公司,德国曼柴油机和涡轮欧洲股份公司的联营公司 | Exhaust valve actuator for large-scale two-stroke diesel engine |
| CN103228878A (en) * | 2010-11-30 | 2013-07-31 | 瓦锡兰芬兰有限公司 | An arrangement and a method of operating a gas exchange valve of an internal combustion engine, a cylinder head and a method of upgrading an internal combustion engine |
| CN103228878B (en) * | 2010-11-30 | 2015-06-24 | 瓦锡兰芬兰有限公司 | An arrangement and a method of operating a gas exchange valve of an internal combustion engine, a cylinder head and a method of upgrading an internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4657311B2 (en) | 2011-03-23 |
| KR20050099602A (en) | 2005-10-14 |
| JP2004084670A (en) | 2004-03-18 |
| JP2008121694A (en) | 2008-05-29 |
| JP2005256843A (en) | 2005-09-22 |
| CN1651725A (en) | 2005-08-10 |
| KR100538679B1 (en) | 2005-12-23 |
| KR20040020003A (en) | 2004-03-06 |
| KR20050033575A (en) | 2005-04-12 |
| CN1314884C (en) | 2007-05-09 |
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