CN102383995B - Passive meter valve and large-sized diesel motor - Google Patents
Passive meter valve and large-sized diesel motor Download PDFInfo
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- CN102383995B CN102383995B CN201110247768.5A CN201110247768A CN102383995B CN 102383995 B CN102383995 B CN 102383995B CN 201110247768 A CN201110247768 A CN 201110247768A CN 102383995 B CN102383995 B CN 102383995B
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- piston
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
- F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0205—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine
- F02M63/0215—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine by draining or closing fuel conduits
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- Safety Valves (AREA)
Abstract
The invention provides a kind of passive meter valve, it is for large-sized diesel motor, this meter valve has valve chest (2), this valve chest has for the entrance (3) of flowable media and outlet (4) and the valve chamber (5) that is arranged between described entrance and described outlet, wherein in valve chamber (5), be provided with valve body (6), this valve body has inlet side closure member (63) and outlet side closure member (64), these closure member are configured to cooperate hermetically with inlet side valve seat (31) and outlet side (41) respectively, wherein said inlet side closure member (63) by spring (8) towards described inlet side valve seat (31) bias voltage, and described meter valve has piston (7), this piston is arranged on described valve body (6) place, and the outside of this piston can be conducted through the wall of described valve chamber (5) slidably.At least one port hole (73) that can flow through for described flowable media is provided with in the end face (71) of described piston (7).
Description
Technical field
The present invention relates to the passive meter valve for large-sized diesel motor, this passive meter valve has valve chest, this valve chest has entrance and exit for flowable media and the valve chamber that is arranged between described entrance and described outlet, wherein in described valve chamber, be provided with valve body, this valve body has inlet side closure member and outlet side closure member, these closure member be configured to respectively with inlet side valve seat and outlet side valve base sealing cooperate, wherein said inlet side closure member by spring towards described inlet side valve seat bias voltage, and described meter valve has piston, this piston is arranged on described valve body place, and the outside of this piston can be conducted through the wall of described valve chamber slidably.The invention still further relates to the large-sized diesel motor with described meter valve.
Background technique
The large-sized diesel motor of two strokes or four stroke engine can be designed to, be usually used in the driver element of boats and ships also for stationary deployment, such as, drive high-rating generator with output electric energy.
In this respect, establishing common rail system for modern large-sized diesel motor provides fuel.Thus, fuel is delivered to storage pressure storehouse by high-pressure service pump, and described storage pressure storehouse is also called accumulator or rail.The fuel with pressure (such as, reaching 1600 bar, even up to 2000 bar) is arranged in described storage pressure storehouse.So the pressurized fuel in self pressure-storage storehouse supplies the fuel nozzle of all cylinders in the future, and fuel is injected in corresponding cylinder by described nozzle.
Be well known that in this respect, corresponding passive meter valve is set between storage pressure storehouse and each fuel nozzle.The purposes of described passive meter valve is, in the corresponding operation cycle, once the fuel of existing prearranging quatity flows into fuel nozzle from storage pressure storehouse, this passive meter valve just closes the circulation between storage pressure storehouse and corresponding fuel nozzle automatically.In this way, just in case there is the danger of leakage or other type, fuel can be avoided to flow out in uncontrollable or less desirable mode.In addition, such as maintenance operation, can circulate under relatively low pressure (such as 2 bar are to 20 bar) at tail-off and fuel, when namely fuel cycle is by storage tank and storage pressure storehouse, remove the communication line between storage pressure storehouse and fuel nozzle, to avoid the blocking of fuel system.
Because fuel is in the high pressure from 1600 bar to 2000 bar, passive meter valve must have well, reliable sealing function.
Known passive meter valve Problems existing in large-sized diesel motor is because the viscosity fluctuation of the viscosity fluctuation especially temperature trigger of fuel causes.Heavy fuel oil is commonly used for the fuel in large-sized diesel motor, and described heavy fuel oil needs the temperature being heated to above 100 degrees Celsius maybe can spray to make it fully can flow due to its very high viscosity usually.But in addition, motor utilizes the low-down marine diesel oil of viscosity to start usually, also utilizes it to close.Generally, boats and ships are when Gangkou District is moved, and motor will operate by marine diesel oil especially, and at off-lying sea, transition is for using heavy fuel oil operation incessantly.But, compared with operating with by heavy fuel oil, by under the low temperature that marine diesel oil running often occurs in fuel system.Due to temperature fluctuation, also there is fluctuation in fuel viscosity.But viscosity-modifying can affect the fuel quantity making passive meter valve close.Such as, if passive meter valve is set as Specific amounts for the first viscosity, so may when another viscosity, after a small amount of fuel flows through, meter valve is just closed, or only after flowing through a large amount of fuel meter valve just can close.
Summary of the invention
The present invention to be intended to this undesirably effect provides corrective measure.Therefore the object of this invention is to provide a kind of passive meter valve for large-sized diesel motor, in this passive meter valve, the fuel quantity making valve automatically close after flowing through has nothing to do with dielectric viscosity substantially.
The subject matter meeting these objects with the feature of independent claims for feature.
According to the present invention, a kind of passive meter valve for large-sized diesel motor, this meter valve has valve chest, this valve chest has entrance and exit for flowable media and the valve chamber that is arranged between described entrance and described outlet, wherein in valve chamber, be provided with valve body, this valve body has inlet side closure member and outlet side closure member, these closure member are configured to cooperate hermetically with inlet side valve seat and outlet side respectively, wherein said inlet side closure member by spring towards described inlet side valve seat bias voltage, and described meter valve has piston, this piston is arranged on described valve body place, and the outside of this piston can be conducted through the wall of described valve chamber slidably.At least one port hole that can flow through for described flowable media is provided with in the end face of described piston.
Valve chamber is divided into cup and rear room by piston, has at least one port hole in the end face of piston, and this port hole provides the flowing between cup and rear room to be communicated with.Because port hole is arranged in the end face of piston, so it can be configured to very short, to make its flow resistance substantially have nothing to do with dielectric viscosity.The through-current capacity consequently making meter valve close completely and dielectric viscosity have nothing to do.
For each port hole, when the length of port hole and the ratio of diameter are 4 to the maximum, the independence with viscosity especially can be ensured.
When inlet side closure member is configured to linearly contact with inlet side valve seat, uses and can realize seal action excellent especially according to meter valve of the present invention.
Due to same reasons, preferably outlet side closure member is configured to linearly contact with outlet side valve seat.
Especially easily can realize described linear contact like this, namely inlet side closure member or outlet side closure member have the spherical surface correspondingly cooperated with inlet side valve seat or outlet side valve seat.
In such configuration, advantageous measure makes the centre of curvature of spherical surface eccentric relative to the longitudinal axis of valve body.Therefore can realize the comparatively small curve of spherical surface, increase the length of linear contact whereby.Therefore, cracking pressure, opens required pressure difference more precisely, can be set as little value.
In a preferred embodiment, inlet side valve seat or outlet side valve seat have trochoidal surface.Can therefore realize particularly preferred sealing effect.
For valve body or two closure member from centering, preferably inlet side closure member and outlet side closure member have same design.
According to preferred embodiment, valve body extends in the inside of spring.This is simple especially design concept.
Each port hole is all relative to being arranged radially at spring outside, and this is favourable in practical.
Prove that the pressure difference be advantageously communicated with for the flowing of opening between inlet side valve seat with inlet side closure member reaches 2 bar to 20 bar in practice.Its reason is, when in cycling, fuel presses circulation time between storehouse at tank and storage, and meter valve should remain on closed state.In cycling, the pressure in storage pressure storehouse usually between 2 bar to 20 bar, such as, reaches 10 bar.Such as, so arrange slightly higher by being used for opening the pressure difference that the flowing between inlet side valve seat with inlet side closure member is communicated with, 15 bar, would not open flow be communicated with like this in cycling.
Preferably piston structure be separate part in configuration aspects and make it to be connected with valve body.
Spring is supported in the end of piston also advantageously.
The present invention also proposes a kind of large-sized diesel motor had according to meter valve of the present invention.
Described meter valve is preferably arranged between the high pressure storage pressure storehouse of fuel and fuel nozzle.
The advantageous measures that the present invention is other and preferred implementation are from dependent claims.
Accompanying drawing explanation
Describe the present invention in detail referring to mode of execution and accompanying drawing, schematic diagram is not drawn to scale, and part shows with section, in the accompanying drawings:
Fig. 1 is the sectional arrangement drawing of the mode of execution by meter valve according to the present invention;
Fig. 2 is the schematic diagram of the common rail system of large-sized diesel motor;
Fig. 3 is the valve body of the mode of execution of Fig. 1; And
Fig. 4 is the valve body being placed with piston of the mode of execution of Fig. 1.
Embodiment
Fig. 1 illustrates the mode of execution according to meter valve of the present invention with elevational schematic, and this meter valve entirety is represented by reference character 1.This section obtains along the longitudinal axis A of meter valve 1.
Meter valve 1 is passive valve, and this refers to the uncontrolled SC sigmal control of this valve or can't help control signal and initiatively activates, but depends on normal pressure difference voluntarily or automatic opening-closing.
Passive meter valve 1 has valve chest 2, and this valve chest is made up of two-part here, comprises bottom 21 and covers or top 22.Top 22 and bottom 21 are mutually permanently connected by multiple screw 23.Valve chest 2 has entrance 3 for flowable media and outlet 4.Valve chamber 5 is arranged between entrance 3 and outlet 4 in valve chest 2, is provided with the valve body 6 that longitudinally A direction extends in this valve chamber.
Fig. 3 shows another schematic diagram of valve body 6 so that understand better.Two axial ends of valve body 6 are formed by two closure member 63,64, i.e. inlet side closure member 63 and outlet side closure member 64.These closure member 63,64 are configured to cooperate in a sealing fashion with inlet side valve seat 31 and outlet side valve seat 41 respectively.Two valve seats 31,41 are arranged in valve chest 2, are namely positioned at the inlet-side end portions of valve chamber 5 or are positioned at the outlet side end portion of valve chamber 5.Valve seat 31,41 can be machined directly in valve chest 2, or as separate part manufacture, then to insert in the respective cut in valve chest 2 and to be fastened on this place, such as fastening by hot charging.According to application, may advantageously as separate part manufacture using valve seat 31,41, because make, for material, there is higher flexibility thus.Such valve seat 31,41 can be made up of the material being different from valve chest 2.
In the present embodiment, inlet side valve seat 31 and outlet side valve seat 41 both have trochoidal surface 32 and 42 respectively, and described trochoidal surface cooperates with inlet side closure member 63 and outlet side closure member 64 respectively.
Valve body 6 is provided with piston 7, and with regard to external diameter, it is dimensioned to and makes outside slidably by the wall of valve chamber 5.Small gap is provided with between the outside of piston 7 and the wall of valve chamber 5.Fig. 4 shows the schematic diagram of the valve body 6 with piston 7, to understand better.Piston 7 is configured to substantial cylindrical, and is arranged so that its column axis is overlapping with longitudinal axis A.Piston 7 has end face 71 in its side towards entrance 3; Another axial end of piston 7 is unlimited.
Valve body 6 and piston 7 can construct as a whole.But, compare from production technology aspect it is possible that valve body 6 and piston 7 are made as two independently parts, link together subsequently.Piston 7 also can be made up of multiple parts, such as, also can be made up of different materials, adapts to ideally apply accordingly or be suitable for simplify manufacture to make its attribute.
In mode of execution described herein, the end face 71 of piston 7 be provided with as receive valve body 6 center cutout 72.Valve body 6 has flange shape teat 65, and it is as the abutting part for end face 71.Valve body 6 is released from inside, until flange shape teat 65 abuts from inner side with end face 71 through the center cutout 72 in end face 71.Thus, the size of these parts is mutually adaptive, makes the inlet side closure member 63 of valve body 6 extend over the end face 71 (see Fig. 4) of piston 7 completely.In mode of execution described herein, piston 7 by hot charging on valve body 6.
According to the present invention, be provided with at least one port hole 73 in the end face 71 of piston, this port hole is parallel to longitudinal axis A and in axial direction extends through end face 71.In mode of execution described herein, be provided with multiple port hole 73.
Each port hole 73 has diameter d and length L, and diameter d refers to the diameter determining flow resistance, is namely generally the minimum diameter of port hole 73.
In addition, be provided with multiple hole 74 in the jacket surface of piston 7, each Kong Jun radially extends through the wall of piston 7.Thus, radial direction refers to direction perpendicular to axial direction, and described axis is determined by longitudinal axis A.Flowable media can flow through hole 74 and arrives the wall of valve chamber 5, with at this such as piston 7 provides lubrication.
As shown in Figure 1, valve body 6 is biased by spring 8 and leans against on inlet side valve seat 31 together with piston 7, makes inlet side closure member 63 be pressed against inlet side valve seat 31.Spring 8 extends and coaxial with valve body 6 vertically, and valve body 6 is extended in the inside of spring 8.On the one hand, spring 8 is supported at valve chest 2 place, and namely near outlet side valve seat 41, on the other hand, this spring is supported to the end of inherent piston 7.
Before the more details of explanation, first explain the operator scheme of meter valve 1.Meter valve 1 is applicable to the common rail system of large-sized diesel motor.In the large-sized diesel motor in modern times, usually there is multiple common rail system, such as, spray, for gas exchanges or for auxiliary system for fuel.Below with reference to the application that fuel sprays.Large-sized diesel motor operates using heavy fuel oil as fuel usually, and namely, flowable media is exactly heavy fuel oil in this example.As other fuel, usually use marine diesel oil, marine diesel oil especially uses when port operations motor, namely before ship leaves harbour or when ship sails port district into, large-sized diesel motor operates by marine diesel oil usually.Utilizing in marine diesel oil operation process, operating temperature is usually remarkable in heavy fuel oil operation process.The fluctuation of fuel viscosity also produces thus.
Meter valve 1 according to the present invention is applicable to heavy fuel oil, therefore also can be used for the common rail system that large-sized diesel motor fuel sprays.Fig. 2 illustrates the schematic diagram of this common rail system of large-sized diesel motor.This system comprises high-pressure service pump 50, and fuel (i.e. heavy fuel oil) is transported in storage pressure storehouse 51 by this high-pressure service pump, and this storage pressure storehouse is also referred to as accumulator or rail.Storage pressure storehouse 51 is configured to usually roughly at the tubular member that the horizontal position of cylinder head extends along motor.Pipeline 52 is pressed storehouse bifurcated out from storage and is caused fuel nozzle 53 to supply this fuel nozzle heavy fuel oil.In fig. 2, illustrate only such pipeline 52 and a fuel nozzle 53, because this is enough to understand this explanation.In storage pressure storehouse, the pressure of heavy fuel oil is roughly suitable with jet pressure.This pressure is such as 1600 bar, but also can be higher, such as, reach 2000 bar.The meter valve 1 being attached to storage pressure storehouse 51 (be such as directly attached to storage pressure storehouse 51 or be attached on storage pressure storehouse 51) is arranged between storage pressure storehouse 51 and pipeline 52.Meter valve 1 is arranged so that its entrance 3 press storehouse 51 to flow to be communicated with storage, and it exports 41 and to flow with pipeline 52 and be communicated with.
As long as fuel nozzle 53 sprays into any fuel not yet in cylinder, meter valve 1 is just in the closed position shown in Fig. 1; In this position, inlet side closure member 63 cooperates hermetically with inlet side valve seat 31, makes heavy fuel oil can not flow through meter valve 1.In this state, at outlet 4 and entrance 3 place, heavy fuel oil has substantially identical hydrodynamic pressure.Spring 8 impels inlet side closure member 63 to slip into hermetically in inlet side valve seat 31.
Once fuel nozzle 53 starts heavy fuel oil to spray in the firing chamber of cylinder, the pressure in pipeline 52 will decline.The rear result that pressure drop brings is: valve body 6 moves up according to illustrating (Fig. 1) together with piston 7, whereby, inlet side closure member 63 lifts from inlet side valve seat 31, makes the heavy fuel oil in self pressure-storage storehouse 51 can through port hole 73 thus by meter valve 1 and can in inflow line 52.The pressure difference needed for flowing connection of opening inlet side valve seat 31 place can be set by different measure, will be further explained below.This pressure difference is advantageously set as the value between 2 bar to 20 bar.This pressure difference is set as the pressure higher than the pressure in storage pressure storehouse 51 during cycling.
When the valve at inlet side valve seat 31 place is communicated with unlatching, therefore the stroke of piston 7 depends on the emitted dose of heavy fuel oil, at least proportional with this emitted dose.Once course of injection terminates, that is, fuel nozzle 53 cuts out, and the pressure in pipeline 52 just increases again.Piston 7 moves whereby, and moves down according to diagram (Fig. 1) under the tension force effect of spring 8, and heavy fuel oil flows out by port hole 73.When inlet side closure member 63 be forced to again enter hermetically in inlet side valve seat 31 time, the above-mentioned mobile end of piston.
When the oil mass of restriking being defined as maximum value flows through meter valve 1, piston 7 reaches its maximum stroke.Meter valve 1 is configured to usually or its size is set to that the maximum stroke of piston 7 is not enough to impel outlet side closure member 64 to enter in outlet side valve seat 41 in the course of injection of conventional or standard usually.
Such as, to leak or malfunctioning if there is fuel nozzle 53 in the downstream of meter valve 1, the heavy fuel oil that the heavy fuel oil so flowing through meter valve 1 flows through more than standard course of injection.This result caused is: piston continues it according to diagram (Fig. 1) and moves up until outlet side closure member 64 is prompted to enter hermetically in outlet side valve seat 41.Once so, heavy fuel oil just can not flow through meter valve 1 again and enter in pipeline 52.
Such as, during maintenance operation, may expect to disassemble pipeline 52 or fuel nozzle 53.Close large-sized diesel motor for this reason.Fuel cooling can make fuel thickness or almost become solid to such an extent as to blocking fuel system, can not cool to make fuel, usually make in cycling from the fuel cycle in tank through storage pressure storehouse 51, and unshowned reflux pipeline is got back in tank in Fig. 2.This cycling is carried out by means of only roughing vacuum pump usually, and that is high-pressure service pump 50 does not start in this cycling.In cycling, the pressure in storage pressure storehouse 51 generally reaches 2 bar to 20 bar, such as 10 bar.
If the pressure in storage pressure storehouse 51 drops to above-mentioned value, pipeline 52 is released pressure, then can splitly lay down.The pressure at outlet 4 place of meter valve 1 reduces thus.But, because the pressure difference for open flow connection between inlet side valve seat 31 and inlet side closure member 63 is set greater than the pressure of cycling, in this case, this pressure difference is roughly set as 15 bar, because pipeline is without pressure, piston does not move but also remains on the operating position shown in Fig. 1.
Especially simple as far as possible in order to make to remove pipeline 52 like this, advantageously the pressure difference being used for open flow connection between inlet side valve seat 31 and inlet side closure member 63 is set as the value between 2 bar to 20 cling to, is namely set greater than the value of the pressure in cycling in storage pressure storehouse 51.Heavy fuel oil can recirculation in a straightforward manner thus.Between 2 bar to 20 cling between pressure difference mean only when according to diagram (Fig. 1) the pressure at entrance 3 place of the pressure ratio meter valve 1 of end face 71 side of bottom little go out between 2 bar to 20 bar between this value time, inlet side closure member 63 is just opened.
Main aspect according to meter valve 1 of the present invention is: in the end face 71 of piston 7, be provided with at least one port hole 73.Due to above-mentioned measure, flow in fuel can be made very short through each port hole 73 of (or passing through when fuel is forced to flow back to), the fluid flow resistance of port hole 73 and the viscosity of fuel have nothing to do whereby.Even if can guarantee when the viscosity fluctuation of fuel like this, the fuel quantity set by meter valve also can keep constant.Therefore, if meter valve 1 is set as specific greatest amount of fuel, so when fuel viscosity changes or when viscosity fluctuation, fuel quantity when reaching maximum value also can be invariable.Have nothing to do with viscosity and mean and can realize very accurate and constant fuel quantity being restricted to particular value, this value also can not affect by any of viscosity fluctuation.
In order to make the fluid flow resistance of port hole have nothing to do with the viscosity flowing through medium, prove particularly advantageously to make the length L of port hole 73 be 4 to the maximum with the ratio of the diameter d of port hole 73.Thus, diameter d refers to the diameter d determining flow resistance, and when diameter changes on length L, this typically has a diameter from very small diameter or minimum diameter.
Because the operation pressure in storage pressure storehouse 51 is very large, such as 1600 bar even reach 2000 bar, between inlet side valve seat 31 and inlet side closure member 63 or correspondingly to realize extraordinary sealing effect between outlet side valve seat 41 and outlet side closure member 64 naturally extremely important.At inlet side closure member 63 or outlet side closure member 64 and especially, both closure member 63,64 are configured to linearly contact with inlet side valve seat 31 or outlet side valve seat 41 respectively, it is particularly advantageous for being proved to be for above-mentioned sealing effect.This linear contact between involved mating member is very effective, especially can Leakage prevention.In addition, the inclination of piston 7 is tolerated in this linear contact very much, even if that is: also can guarantee high sealing effect when piston 7 slight inclination or misorientation.
In mode of execution described herein, because inlet side closure member 63 and outlet side closure member 64 all have the spherical surface 631 or 641 cooperated with inlet side valve seat 31 or the respective corresponding trochoidal surface 32 or 42 of outlet side valve seat 41 respectively, therefore achieve linear contact at inlet side valve seat 31 with both outlet side valve seats 41 place.
Linear contact relative to axis position influence for open corresponding flowing be communicated with needed for pressure difference.Such as, in inlet side valve seat 31, with regard to the diagram of Fig. 1, linear contact is higher relative to the position of axis, and the length of the linear contact that whole periphery is measured is larger.The length of linear contact is longer, and the pressure difference opened needed for corresponding flowing connection is less.Therefore, the pressure difference of opening when corresponding flowing is communicated with can set respectively on the position of the linear contact of spherical surface 631 or 641.
Because preferred pressure difference is relatively little, be 2 bar to 20 bar, so advantageously make the length of linear contact larger.This especially realizes by making the centre of curvature M of spherical surface 631 or 641 eccentric relative to the longitudinal axis A of valve body 6 respectively.This refers to, centre of curvature M (in this case the center of the spheroid at difference place, ball surface 631 or 641) is positioned at and is parallel to longitudinal axis A and has on the straight line K of spacing e with longitudinal axis A.Be positioned at centre of curvature compared with the situation in longitudinal axis A, less curvature can be obtained by this measure.
In many cases, with regard to actual enforceability, curvature is relatively little; But advantageously curvature should greatly to guaranteeing that surface 631 and 641 contacts with linear between trochoidal surface 32 and 42 respectively.For given curvature, the length of separately linear contact and the consequent pressure difference be communicated with for open flow set by the size of spacing e.
Another measure that can affect or set for opening the pressure difference that respective flow is communicated with is the elastic characteristic selecting spring 8, specifically selects the spring constant of spring 8.
Another advantageous measures makes inlet side closure member 63 and outlet side closure member 64 at least with regard to the surface cooperated with corresponding valve seat 31,41, have same configuration.By this symmetry properties can realize valve body 6 from centering effect.The simple centering of valve body 6 can be realized by the micro-gap between the jacket surface of piston 7 and the wall of valve chamber 5.
Linear contact between inlet side closure member 63 with inlet side valve seat 31 or correspondingly between outlet side closure member 64 with outlet side valve seat 41 also realizes by other geometry mode of execution on corresponding cooperation surface.Such as, two cooperation surfaces all can be configured to spherical surface, or two cooperation surfaces all can be configured to trochoidal surface, especially have the trochoidal surface of different cone angle.
As has been mentioned, all port holes 73 are preferably relative to the outside being positioned at spring 8 axially, namely for each port hole, the half that the spacing between the central axis of port hole 73 and longitudinal axis A is greater than the external diameter of spring 8 adds the radius of corresponding port hole 73 in the outer surface of the end face 71 of piston.
Claims (15)
1. the passive meter valve for large-sized diesel motor, this passive meter valve has valve chest (2), this valve chest has for the entrance (3) of flowable media and outlet (4) and the valve chamber (5) that is arranged between described entrance and described outlet, wherein in described valve chamber (5), be provided with valve body (6), this valve body has inlet side closure member (63) and outlet side closure member (64), these closure member are configured to cooperate hermetically with inlet side valve seat (31) and outlet side valve seat (41) respectively, wherein said inlet side closure member (63) by spring (8) towards described inlet side valve seat (31) bias voltage, and described meter valve has piston (7), this piston is arranged on described valve body (6) place, and the outside of this piston can be conducted through the wall of described valve chamber (5) slidably, the feature of described meter valve is, at least one port hole (73) that can flow through for described flowable media is provided with in the end face (71) of described piston (7).
2. meter valve according to claim 1, wherein, for each port hole (73), the length (L) of described port hole (73) and the ratio of diameter (d) are 4 to the maximum.
3. meter valve according to claim 1 and 2, wherein, described inlet side closure member (63) is configured to linearly contact with described inlet side valve seat (31).
4. meter valve according to claim 1 and 2, wherein, described outlet side closure member (64) is configured to linearly contact with described outlet side valve seat (41).
5. meter valve according to claim 1 and 2, wherein, described inlet side closure member (63) or described outlet side closure member (64) have the spherical surface (631,641) correspondingly cooperated with described inlet side valve seat (31) or described outlet side valve seat (41).
6. meter valve according to claim 5, wherein, the centre of curvature (M) of described spherical surface (631,641) is eccentric relative to the longitudinal axis (A) of described valve body (6).
7. meter valve according to claim 1 and 2, wherein, described inlet side valve seat (31) or described outlet side valve seat (41) have trochoidal surface (32,42).
8. meter valve according to claim 1 and 2, wherein, described inlet side closure member (63) has identical design with described outlet side closure member (64).
9. meter valve according to claim 1 and 2, wherein, described valve body (6) extends in the inside of described spring (8).
10. meter valve according to claim 1 and 2, wherein, each port hole (73) puts the outside in described spring (8) relative to radial equipartition.
11. meter valves according to claim 1 and 2, wherein, the pressure difference that the flowing for opening between described inlet side valve seat (31) with described inlet side closure member (63) is communicated with reaches 2 bar to 20 bar.
12. meter valves according to claim 1 and 2, wherein, described piston (7) is configured to separate part, and is connected with described valve body (6).
13. meter valves according to claim 1 and 2, wherein, described spring (8) is supported at described end face (71) place of described piston (7).
14. 1 kinds of large-sized diesel motors with the meter valve according to aforementioned arbitrary claim.
15. large-sized diesel motors according to claim 14, wherein, described meter valve is arranged between high pressure storage pressure storehouse (51) of fuel and fuel nozzle (53).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP10174196.5 | 2010-08-26 | ||
| EP10174196 | 2010-08-26 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102383995A CN102383995A (en) | 2012-03-21 |
| CN102383995B true CN102383995B (en) | 2016-04-27 |
Family
ID=43085844
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110247768.5A Expired - Fee Related CN102383995B (en) | 2010-08-26 | 2011-08-25 | Passive meter valve and large-sized diesel motor |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP2423498B1 (en) |
| JP (1) | JP5881981B2 (en) |
| KR (1) | KR101917389B1 (en) |
| CN (1) | CN102383995B (en) |
| DK (1) | DK2423498T3 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AT513158B1 (en) * | 2012-04-10 | 2014-03-15 | Bosch Gmbh Robert | Flow restrictor with ball and throttle |
| CN103016426B (en) * | 2012-12-06 | 2016-01-20 | 联合汽车电子有限公司 | Be integrated with the jet pump nozzle of Decompression valves |
| DE102013210983B4 (en) * | 2013-06-12 | 2021-04-29 | Mtu Friedrichshafen Gmbh | Flow control valve |
| DE102014105439B4 (en) | 2014-04-16 | 2020-03-26 | Woodward L'orange Gmbh | Flow control valve for a dual fuel fuel injection system |
| WO2015177399A1 (en) * | 2014-05-22 | 2015-11-26 | Wärtsilä Finland Oy | Connecting element |
| EP3023628B8 (en) | 2014-11-21 | 2017-04-19 | O.M.T. Officine Meccaniche Torino S.p.A. | A fuel flow limiting valve for large internal combustion engines |
| DE102016101425B4 (en) | 2016-01-27 | 2018-05-09 | Firma L'orange Gmbh | Quantity limiting valve, in particular for a high-pressure pump system |
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| ES445020A1 (en) * | 1976-02-10 | 1977-06-01 | Bendiberica Sa | Pressure limiting valve with movable piston - has spherical seal attached to piston with stops limiting linear movement |
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2011
- 2011-06-10 EP EP11169400.6A patent/EP2423498B1/en not_active Not-in-force
- 2011-06-10 DK DK11169400.6T patent/DK2423498T3/en active
- 2011-06-29 JP JP2011144527A patent/JP5881981B2/en not_active Expired - Fee Related
- 2011-08-22 KR KR1020110083454A patent/KR101917389B1/en active IP Right Grant
- 2011-08-25 CN CN201110247768.5A patent/CN102383995B/en not_active Expired - Fee Related
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| DE19548610A1 (en) * | 1995-12-23 | 1997-06-26 | Bosch Gmbh Robert | Flow limiting valve for fuel injection system |
| CN1395035A (en) * | 2001-06-27 | 2003-02-05 | 瓦特西拉技术有限公司 | Cut-off valve for fuel system |
| CN1738967A (en) * | 2003-01-15 | 2006-02-22 | 瓦特西拉芬兰有限公司 | Arrangement in fuel injection apparatus |
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Also Published As
| Publication number | Publication date |
|---|---|
| JP2012047170A (en) | 2012-03-08 |
| JP5881981B2 (en) | 2016-03-09 |
| EP2423498B1 (en) | 2013-09-11 |
| CN102383995A (en) | 2012-03-21 |
| DK2423498T3 (en) | 2013-12-09 |
| KR20120020056A (en) | 2012-03-07 |
| EP2423498A1 (en) | 2012-02-29 |
| KR101917389B1 (en) | 2018-11-09 |
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