CN102383995A - Passive flow control valve - Google Patents
Passive flow control valve Download PDFInfo
- Publication number
- CN102383995A CN102383995A CN2011102477685A CN201110247768A CN102383995A CN 102383995 A CN102383995 A CN 102383995A CN 2011102477685 A CN2011102477685 A CN 2011102477685A CN 201110247768 A CN201110247768 A CN 201110247768A CN 102383995 A CN102383995 A CN 102383995A
- Authority
- CN
- China
- Prior art keywords
- valve
- closure member
- inlet side
- piston
- valve seat
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000000446 fuel Substances 0.000 claims abstract description 61
- 230000009969 flowable effect Effects 0.000 claims abstract description 9
- 238000003860 storage Methods 0.000 claims description 30
- 239000010763 heavy fuel oil Substances 0.000 description 21
- 230000001351 cycling effect Effects 0.000 description 10
- 230000000694 effects Effects 0.000 description 7
- 239000010759 marine diesel oil Substances 0.000 description 7
- 238000007789 sealing Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 230000002349 favourable effect Effects 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- 239000007921 spray Substances 0.000 description 4
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 239000012530 fluid Substances 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 230000003044 adaptive effect Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000010304 firing Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
Classifications
-
- 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
-
- 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
-
- 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
-
- 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
-
- 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
Landscapes
- 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 passive flow control valve (1) has valve housing (2) with an inlet (3) and an outlet (4) for a flowable medium. A valve chamber (5) is arranged between the inlet and outlet. An input-side closing element is pre-stressed by a spring (8) against an input-side valve seat (31). A piston (7) is provided on a valve body (6), where outer side of the piston is guided through the wall of the valve chamber in sliding manner. A passage hole (73) is provided in an end face of the piston through which the flowable medium flows. An independent claim is also included for a large diesel engine with flow control valve that is arranged between a high-pressure reservoir for a fuel and a fuel injector nozzle.
Description
Technical field
The present invention relates to according to the passive meter valve that is used for large-sized diesel motor that belongs to the preamble of such other independent claims.The invention still further relates to large-sized diesel motor with said meter valve.
Background technique
Can be designed to the large-sized diesel motor of two strokes or four stroke engine, the driver element that is usually used in boats and ships also is used for static operation, for example drives high-rating generator with the output electric energy.
In this respect, having set up common rail system comes for modern large-sized diesel motor fuel to be provided.Thus, fuel is delivered to storage through high-pressure service pump and presses the storehouse, and said storage presses the storehouse also to be called accumulator or rail.Fuel with pressure (for example, reach 1600 crust, even cling to up to 2000) is arranged in said storage and presses the storehouse.So the pressurized fuel in self pressure-storage storehouse is supplied with the fuel nozzle of all cylinders in the future, said nozzle is injected fuel in the corresponding cylinder.
Be well known that in this respect, press between storehouse and each fuel nozzle in storage corresponding passive meter valve is set.The purposes of said passive meter valve is that in the cycle, in case the fuel of existing prearranging quatity presses the storehouse to flow into fuel nozzle from storage, this passive meter valve is just closed storage automatically and pressed the circulation between storehouse and the corresponding fuel nozzle in corresponding work.In this way, just in case the danger of leakage or other type takes place, can avoid fuel to flow out with mode uncontrollable or that do not expect.In addition; For example, can circulate down at relatively low pressure (for example 2 clinging to 20 crust) at tail-off and fuel, i.e. when fuel cycle is pressed the storehouse through storage tank with storage for maintenance operation; Remove storage and press the communication line between storehouse and the fuel nozzle, to avoid the obstruction of fuel system.
Because fuel is in the high pressure that clings to 2000 crust from 1600, passive meter valve must have well, reliable sealing function.
The problem that known passive meter valve in the large-sized diesel motor exists be since the viscosity fluctuation of fuel especially the viscosity fluctuation of temperature trigger cause.Heavy fuel oil is commonly used makes the fuel in the large-sized diesel motor, and said heavy fuel oil is because its very high viscosity and need be heated to above 100 degrees centigrade temperature usually so that it fully can flow maybe can spray.Yet in addition, motor utilizes the low-down marine diesel oil starting of viscosity usually, also utilizes it to close.Generally speaking, when boats and ships moved at Gangkou District, motor will turn round by marine diesel oil especially, and at off-lying sea, transition is for using the heavy fuel oil operation incessantly.Yet, and compare by heavy fuel oil running, running often occurs under the low temperature in the fuel system by marine diesel oil.Because temperature fluctuation, also there is fluctuation in fuel viscosity.Yet viscosity-modifying can influence the fuel quantity that passive meter valve is closed.For example, if passive meter valve is set at concrete amount to first viscosity, so maybe be when another viscosity, meter valve is just closed after small amount of fuel flows through, perhaps only after flowing through a large amount of fuel meter valve just can close.
Summary of the invention
The present invention is intended to this not, and desired effects provides corrective measure.Therefore the purpose of this invention is to provide a kind of passive meter valve that is used for large-sized diesel motor, in this passive meter valve, the fuel quantity that valve cuts out automatically is irrelevant with dielectric viscosity basically.
Satisfy the be characterized as characteristic of the subject matter of these purposes with independent claims.
According to the present invention; A kind of passive meter valve that is used for large-sized diesel motor; This meter valve has valve chest, this valve chest have the entrance and exit that is used for flowable media and be arranged on said inlet and said outlet between valve chamber, 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 respectively cooperate hermetically with inlet side valve seat and outlet side, and towards said inlet side valve seat bias voltage, and said meter valve has piston to wherein said inlet side closure member by spring; This piston is arranged on said valve body place, and the outside of this piston can be conducted through the wall of said valve chamber slidably.In said piston end face, be provided with at least one port hole that can supply said flowable media to flow through.
Valve chamber is divided into cup and chamber, back by piston, in piston end face, has at least one port hole, and this port hole provides the mobile connection between cup and the chamber, back.Because port hole is arranged in the piston end face, so that it can be configured to is very short, so that make its flow resistance irrelevant with dielectric viscosity basically.Through-current capacity and dielectric viscosity that meter valve is closed fully are irrelevant.
For each port hole, when the ratio of the length of port hole and diameter is 4 to the maximum, especially can guarantee independence with viscosity.
When the inlet side closure member is configured to contact with the inlet side valve seat is linear, uses according to meter valve of the present invention and can realize the seal action of excellence especially.
Because same reasons, preferably the outlet side closure member is configured to contact with the outlet side valve seat is linear.
Can especially easily realize said linear contact like this, promptly inlet side closure member or outlet side closure member have correspondingly the spherical surface with inlet side valve seat or the cooperation of outlet side valve seat.
In this structure, advantageous measure is to make the centre of curvature of spherical surface eccentric with respect to the longitudinal axis of valve body.Therefore can realize spherical surface than small curve, increase the length of linear contact whereby.Therefore, cracking pressure is opened required pressure difference more precisely, can be set at little value.
In a preferred embodiment, inlet side valve seat or outlet side valve seat have trochoidal surface.Can therefore realize good especially sealing effect.
For valve body or its two closure member preferably inlet side closure member and outlet side closure member have same design from centering.
According to preferred embodiment, valve body extends in the inside of spring.This is simple especially design concept.
Each port hole is all outside at spring with respect to radial arrangement, and this is favourable aspect practical.
Proof advantageously is used to open inlet side valve seat and the mobile pressure difference that is communicated with between the inlet side closure member and reaches 2 and cling to 20 and cling in practice.Its reason is that when in cycling, fuel is pressed circulation time between the storehouse at tank and storage, and meter valve should remain on closed state.In cycling, storage presses the pressure in the storehouse to cling between 20 crust between 2 usually, for example reaches 10 crust.So, will be used to open the inlet side valve seat and be provided with slightly higherly with the mobile pressure difference that is communicated with between the inlet side closure member, for example 15 crust just can open flow not be communicated with in cycling like this.
Be separate part preferably and make it to be connected in structure aspects with valve body with piston structure.
Spring is supported at the piston end face place also advantageously.
The present invention also proposes a kind of large-sized diesel motor that has according to meter valve of the present invention.
Said meter valve preferably is arranged on the high pressure storage of fuel and presses between storehouse and the fuel nozzle.
Favourable measure that the present invention is other and preferred implementation are from dependent claims.
Description of drawings
Following schematic representation is not in scale to be drawn with reference to mode of execution and the present invention of accompanying drawing detailed description, and part is with the section demonstration, in the accompanying drawings:
Fig. 1 is through the sectional arrangement drawing according to the mode of execution of meter valve of the present invention;
Fig. 2 is the schematic representation 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 that is 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 the vertical profile schematic representation, and this meter valve integral body is by reference character 1 expression.This section obtains along the longitudinal axis A of meter valve 1.
Meter valve 1 is a passive valve, and this is meant the uncontrolled SC sigmal control of this valve or can't help the control signal positive actuation, 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 lid or top 22.Top 22 is mutually permanently connected by a plurality of screws 23 with bottom 21.Valve chest 2 has the inlet 3 and outlet 4 that is used for flowable media.Valve chamber 5 is arranged on inlet 3 and exports between 4 in valve chest 2, in this valve chamber, be provided with the valve body 6 that extends along the longitudinal axis A direction.
Fig. 3 shows another schematic representation 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 with sealing means with inlet side valve seat 31 and outlet side valve seat 41 respectively.Two valve seats 31,41 are arranged in the valve chest 2, promptly are positioned at the inlet side end of valve chamber 5 or are positioned at the outlet side end of valve chamber 5.Valve seat 31,41 can be machined directly in the valve chest 2, perhaps as the separate part manufacturing, inserts in the respective cut in the valve chest 2 then and is fastened on this place, and is for example fastening through hot charging.According to application, maybe be more favourable with valve seat 31,41 as the separate part manufacturing, for material, have higher flexibility because make thus.Valve seat 31,41 can be processed by the material that is different from valve chest 2 like this.
In current mode of execution, inlet side valve seat 31 has trochoidal surface 32 and 42 respectively with outlet side valve seat 41 boths, and said trochoidal surface is cooperated with inlet side closure member 63 and outlet side closure member 64 respectively.
Valve body 6 is provided with piston 7, and it is dimensioned to the wall that makes the outside pass through valve chamber 5 slidably with regard to external diameter.Between the wall of the outside of piston 7 and valve chamber 5, be provided with small gap.Fig. 4 shows the schematic representation of the valve body 6 that has piston 7, so that understand better.Piston 7 is configured to substantial cylindrical, and is arranged such that its column axis and longitudinal axis A are overlapping.Piston 7 has end face 71 in its side towards inlet 3; Another axial end of piston 7 opens wide.
In the mode of execution described herein, the end face 71 of piston 7 is provided with the center cutout 72 as the usefulness of admitting valve body 6.Valve body 6 has flange shape teat 65, and it is as the abutting part that is used for end face 71.The center cutout 72 that valve body 6 passes in the end face 71 is released internally, up to flange shape teat 65 from inboard and end face 71 butts.Thus, the size of these parts is adaptive each other, makes the inlet side closure member 63 of valve body 6 stretch out end face 71 (see figure 4)s above piston 7 fully.In the mode of execution described herein, piston 7 by hot charging to valve body 6.
According to the present invention, in piston end face 71, be provided with at least one port hole 73, this port hole is parallel to longitudinal axis A and in axial direction extends through end face 71.In the mode of execution described herein, be provided with a plurality of port holes 73.
Each port hole 73 has diameter d and length L, and diameter d is meant the diameter of decision flow resistance, just is generally the minimum diameter of port hole 73.
In addition, be provided with a plurality of holes 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 is said axially definite by longitudinal axis A.Flowable media can flow through hole 74 and arrive the wall of valve chamber 5, for example being that piston 7 provides lubricated at this.
As shown in Figure 1, valve body 6 leans against on the inlet side valve seat 31 through spring 8 biasings with piston 7, makes inlet side closure member 63 press inlet side valve seat 31.Spring 8 extends vertically and is coaxial with valve body 6, makes valve body 6 extend in the inside of spring 8.On the one hand, spring 8 is supported at valve chest 2 places, and promptly near outlet side valve seat 41, on the other hand, this spring is supported to the end of inherent piston 7.
Before explaining more details, at 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, there are a plurality of common rail systems usually, for example are used for fuel and spray, be used for gas exchange or be used for auxiliary system.The application of below reference fuel being sprayed.Usually with the heavy fuel oil running that acts as a fuel, just, flowable media is exactly a heavy fuel oil to large-sized diesel motor in this example.As other fuel, usually use marine diesel oil, marine diesel oil especially uses when harbour operation motor, just before ship leaves the harbour or when ship sailed harbor district into, large-sized diesel motor turned round by marine diesel oil usually.In utilizing the marine diesel oil operation process, operating temperature significantly is lower than the heavy fuel oil operation process usually.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 representation of this common rail system of large-sized diesel motor.This system comprises high-pressure service pump 50, and fuel (being heavy fuel oil) is transported to storage by this high-pressure service pump and presses in the storehouse 51, and this storage presses the storehouse to be also referred to as accumulator or rail.Storage presses storehouse 51 to be configured to the tubular member that roughly extends along motor in the horizontal position of cylinder head usually.Bifurcated comes out and causes fuel nozzle 53 to supply with this fuel nozzle heavy fuel oil pipeline 52 from storage pressure storehouse.In Fig. 2, only show such pipeline 52 and a fuel nozzle 53, because this is enough to understand this explanation.Press the pressure of heavy fuel oil in the storehouse roughly suitable in storage with jet pressure.This pressure for example is 1600 crust, but also can be higher, for example reaches 2000 crust.Being attached to storage presses the meter valve 1 in storehouse 51 (for example directly be attached to store up to press storehouse 51 or be attached at storage and press on the storehouse 51) to be arranged between storage pressure storehouse 51 and the pipeline 52.Meter valve 1 is arranged so that its inlet 3 and storage press storehouse 51 to flow and are communicated with, and it exports 41 and 52 mobile connections of pipeline.
As long as fuel nozzle 53 does not spray into any fuel yet in cylinder, meter valve 1 just is in closed position shown in Figure 1; In this position, inlet side closure member 63 is cooperated with inlet side valve seat 31 hermetically, makes heavy fuel oil can not flow through meter valve 1.In this state, at outlet 4 and inlet 3 places, heavy fuel oil has identical substantially hydrodynamic pressure.Spring 8 impels inlet side closure member 63 to slip into hermetically in the inlet side valve seat 31.
In case fuel nozzle 53 begins heavy fuel oil is sprayed in the firing chamber of cylinder, the pressure in the pipeline 52 will descend.The back result that pressure decline brings is: valve body 6 moves up according to diagram (Fig. 1) with piston 7; Whereby; Inlet side closure member 63 lifts from inlet side valve seat 31, thereby but makes the heavy fuel oil in self pressure-storage storehouse 51 can pass port hole 73 through in meter valve 1 and the inflow line 52.Opening the required pressure difference of mobile connection at inlet side valve seat 31 places can be set by different measure, will do further explanation below.This pressure difference advantageously is set at the value between 2 crust to 20 crust.This pressure difference is set at than storage during cycling and presses the high pressure of pressure in the storehouse 51.
The valve at inlet side valve seat 31 places is communicated with when opening, and therefore the stroke of piston 7 depends on the emitted dose of heavy fuel oil, proportional with this emitted dose at least.In case course of injection finishes, that is, fuel nozzle 53 cuts out, and the pressure in the pipeline 52 just increases again.Piston 7 moves whereby, and under the tension force effect of spring 8, moves down according to diagram (Fig. 1), and heavy fuel oil can flow out through port hole 73.When inlet side closure member 63 is forced to when getting in the inlet side valve seat 31 hermetically the above-mentioned mobile end of piston again.
When confirming as the peaked oil mass of restriking and flow through meter valve 1, piston 7 reaches its maximum stroke.Meter valve 1 is configured to usually or its size is set for usually in the course of injection of routine or standard, and the maximum stroke of piston 7 is not enough to impel outlet side closure member 64 to get in the outlet side valve seat 41.
For example, if take place in the downstream of meter valve 1 that fuel nozzle 53 leaks or malfunctioning, flow through the heavy fuel oil that the heavy fuel oil of meter valve 1 flows through more than the standard course of injection so.This result who causes is: piston continues it according to diagram (Fig. 1) and moves up to be impelled up to outlet side closure member 64 and get into hermetically in the outlet side valve seat 41.In case like this, heavy fuel oil just can not be flowed through in the meter valve 1 entering pipeline 52 again.
For example, during maintenance operation, possibly expect to disassemble pipeline 52 or fuel nozzle 53.Close large-sized diesel motor for this reason.To such an extent as to the fuel cooling can make the fuel thickness or almost become solid to stop up fuel system; For fuel can not cooled off; In cycling, make usually from the fuel cycle in the tank and press storehouse 51, and get back in the tank through unshowned reflux pipeline among Fig. 2 through storage.This cycling is only carried out through roughing vacuum pump usually, that is to say that high-pressure service pump 50 does not start in this cycling.In cycling, storage is pressed the pressure in the storehouse 51 generally to reach 2 and is clung to 20 crust, for example 10 crust.
If storage presses the pressure in the storehouse 51 to drop to above-mentioned value, pipeline 52 is released pressure, can be disassembled then.The pressure at outlet 4 places of meter valve 1 reduces thus.Yet; Because the pressure difference that is used for the open flow connection between inlet side valve seat 31 and the inlet side closure member 63 is set at the pressure greater than cycling; In this case; This pressure difference roughly is set at 15 crust, because pipeline does not have pressure, piston does not move but remains on the operating position shown in Fig. 1 yet.
Especially in order to make such dismounting pipeline 52 simple as far as possible; Advantageously the pressure difference that is used for the open flow connection between inlet side valve seat 31 and the inlet side closure member 63 is set at the value between 2 crust to 20 crust, promptly is set at the value of pressing the pressure in the storehouse 51 greater than storage in the cycling.Heavy fuel oil can be with simple mode recirculation thus.Only mean that between the pressure difference between 2 crust to 20 crust inlet side closure member 63 is just opened when going out between this value between 20 cling to of 2 crust for a short time according to diagram (Fig. 1) pressure at inlet 3 places of the pressure ratio meter valve 1 of end face 71 sides of bottom.
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.Because above-mentioned measure, can make flow through each port hole 73 of when flowing back to (perhaps fuel is compelled through) of fuel very short, the viscosity of the fluid flow resistance of port hole 73 and fuel has nothing to do whereby.Even can guarantee like this when the viscosity fluctuation of fuel, it is constant that the fuel quantity that meter valve sets also can keep.Therefore, if meter valve 1 is set at specific greatest amount of fuel, during so when the fuel viscosity-modifying or when viscosity fluctuation, the fuel quantity when reaching maximum value also can be invariable.Can realize very accurate and constant fuel quantity being restricted to particular value with irrelevant meaning of viscosity, this value is not influenced by any of viscosity fluctuation can yet.
Irrelevant for the fluid flow resistance that makes port hole with the viscosity of the medium of flowing through, proved that particularly advantageous is the length L that makes port hole 73 and the ratio of the diameter d of port hole 73 is 4 to the maximum.Thus, diameter d is meant the diameter d of decision flow resistance, and under situation about changing on the length L, this typically has a diameter from very small diameter or minimum diameter at diameter.
Because storage presses the operation pressure in the storehouse 51 very big; For example 1600 crust even reach 2000 crust between inlet side valve seat 31 and the inlet side closure member 63 or are correspondingly realizing between outlet side valve seat 41 and outlet side closure member 64 that extraordinary sealing effect is extremely important naturally.At inlet side closure member 63 or outlet side closure member 64 and especially closure member 63,64 the two be configured to respectively with inlet side valve seat 31 or outlet side valve seat 41 linear situation about contacting under, it is particularly advantageous being proved to be for above-mentioned sealing effect.This linear contact between the related mating member is very effective, especially can prevent heads.In addition, the inclination of piston 7 is tolerated in this linear contact very much, even that is: under the situation of piston 7 slight inclination or misorientation, also can guarantee the high sealing effect.
In the mode of execution described herein; Because inlet side closure member 63 and outlet side closure member 64 all have respectively and inlet side valve seat 31 or the outlet side valve seat 41 corresponding trochoidal surface 32 separately or the spherical surface 631 or 641 of 42 cooperations, have therefore realized linear the contact at inlet side valve seat 31 with outlet side valve seat 41 the two place.
Linear exposure phase is used to open corresponding flowing for axial position influence and is communicated with required pressure difference.For example, in inlet side valve seat 31, with regard to the diagram of Fig. 1, linear exposure phase is high more for axial position, and the length of the linearity contact of on whole periphery, measuring is big more.The length of linear contact is long more, and it is more little to open the corresponding required pressure difference of connection that flows.Therefore, opening the corresponding pressure difference that flows when being communicated with can set respectively on the linear position contacting of spherical surface 631 or 641.
Because the preferred pressure difference is less relatively, be 2 to cling to 20 crust, so advantageously make the length of linear contact bigger.This especially can realize with respect to the longitudinal axis A of valve body 6 is eccentric respectively through the centre of curvature M that makes spherical surface 631 or 641.This is meant, centre of curvature M (being the center of the spheroid at place respectively, ball property surface 631 or 641 at this) is positioned at and is parallel to longitudinal axis A and has on the straight line K of spacing e with longitudinal axis A.Compare with the situation that centre of curvature is positioned on the longitudinal axis A, can obtain littler curvature through this measure.
In many cases, with regard to actual enforceability, curvature is less relatively; Yet, advantageously curvature should be greatly to guarantee surface 631 and 641 respectively with trochoidal surface 32 and 42 between linearity contact.For given curvature, the length of linear contact and the consequent pressure difference that is used for the open flow connection can be set through the size of spacing e separately.
Can influence or set another measure that is used to open the pressure difference that respective flow is communicated with is the elastic characteristic of selecting spring 8, specifically is the spring constant of selecting spring 8.
Another favourable measure is to make inlet side closure member 63 and outlet side closure member 64 at least just with regard to the surface of corresponding valve seat 31,41 cooperations, have same configuration.Through this symmetry properties can realize valve body 6 from the centering effect.The simple centering that micro-gap between the jacket surface through piston 7 and the wall of valve chamber 5 can be realized valve body 6.
Between inlet side closure member 63 and the inlet side valve seat 31 or correspondingly outlet side closure member 64 contacts also and can realize through other how much mode of executions on corresponding cooperation surface with linearity between the outlet side valve seat 41.For example, two cooperation surfaces all can be configured to spherical surface, and perhaps two cooperation surfaces all can be configured to trochoidal surface, especially have the trochoidal surface of different cone angle.
As already mentioned; All port holes 73 preferably are positioned at the outside of spring 8 with respect to axial; Just for each port hole, the central axis of port hole 73 and the spacing between the longitudinal axis A add the radius of corresponding port hole 73 in the outer surface of piston end face 71 greater than half of the external diameter of spring 8.
Claims (15)
1. passive meter valve that is used for large-sized diesel motor; This passive meter valve has valve chest (2); This valve chest have the inlet (3) that is used for flowable media and outlet (4) and be arranged on said inlet and said outlet between valve chamber (5); Wherein in said valve chamber (5), be provided with valve body (6), this valve body has inlet side closure member (63) and outlet side closure member (64), and these closure member are configured to respectively cooperate hermetically with inlet side valve seat (31) and outlet side valve seat (41); Wherein said inlet side closure member (63) by spring (8) towards said inlet side valve seat (31) bias voltage; And said meter valve has piston (7), and this piston is arranged on said valve body (6) and locates, and the outside of this piston can be conducted through the wall of said valve chamber (5) slidably; Said meter valve is characterised in that, in the end face (71) of said piston (7), is provided with at least one port hole (73) that can supply said flowable media to flow through.
2. meter valve according to claim 1, wherein, for each port hole (73), the length (L) of said port hole (73) is 4 to the maximum with the ratio of diameter (d).
3. meter valve according to claim 1 and 2, wherein, said inlet side closure member (63) is configured to contact with said inlet side valve seat (31) is linear.
4. according to the described meter valve of aforementioned arbitrary claim, wherein, said outlet side closure member (64) is configured to contact with said outlet side valve seat (41) is linear.
5. according to the described meter valve of aforementioned arbitrary claim; Wherein, Said inlet side closure member (63) or said outlet side closure member (64) have correspondingly the spherical surface (631,641) with said inlet side valve seat (31) or said outlet side valve seat (41) cooperation.
6. meter valve according to claim 5, wherein, the centre of curvature (M) of said spherical surface (631,641) is with respect to longitudinal axis (A) off-centre of said valve body (6).
7. according to the described meter valve of aforementioned arbitrary claim, wherein, said inlet side valve seat (31) or said outlet side valve seat (41) have trochoidal surface (32,42).
8. according to the described meter valve of aforementioned arbitrary claim, wherein, said inlet side closure member (63) has identical design with said outlet side closure member (64).
9. according to the described meter valve of aforementioned arbitrary claim, wherein, said valve body (6) extends in the inside of said spring (8).
10. according to the described meter valve of aforementioned arbitrary claim, wherein, each port hole (73) is put the outside in said spring (8) with respect to radial equipartition.
11., wherein, be used to open said inlet side valve seat (31) and reach 2 with the mobile pressure difference that is communicated with between the said inlet side closure member (63) and cling to 20 crust according to the described meter valve of aforementioned arbitrary claim.
12. a meter valve, wherein said piston (7) is configured to separate part, and is connected with said valve body (6).
13. according to the described meter valve of aforementioned arbitrary claim, wherein, said spring (8) is located supported at the said end face (71) of said piston (7).
14. large-sized diesel motor that has according to the described meter valve of aforementioned arbitrary claim.
15. large-sized diesel motor according to claim 14, wherein, said meter valve is arranged in the high pressure storage of fuel and presses between storehouse (51) and the 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 true CN102383995A (en) | 2012-03-21 |
| CN102383995B 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) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103016426A (en) * | 2012-12-06 | 2013-04-03 | 联合汽车电子有限公司 | Jet pump nozzle integrating pressure relief valve |
| CN105264216A (en) * | 2013-06-12 | 2016-01-20 | Mtu腓特烈港有限责任公司 | Quantity-limiting valve |
| CN105626341A (en) * | 2014-11-21 | 2016-06-01 | Omt都灵机械车间有限公司 | A fuel flow limiting valve for large internal combustion engines |
Families Citing this family (4)
| 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 |
| 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 |
| DE102016101425B4 (en) | 2016-01-27 | 2018-05-09 | Firma L'orange Gmbh | Quantity limiting valve, in particular for a high-pressure pump system |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| DE102005012165A1 (en) * | 2005-03-17 | 2006-09-28 | L'orange Gmbh | Fuel storage for fuel injection system of internal combustion engine of motor vehicle, has segments, of which two are connected with remaining for supplying fuel over linking lines, if break or leakage occurs in one segment |
| WO2007014733A1 (en) * | 2005-08-02 | 2007-02-08 | L'orange Gmbh | Fuel injection system for an internal combustion engine |
| CN1985088A (en) * | 2004-07-30 | 2007-06-20 | 西门子公司 | Valve for use in a fuel line of a motor vehicle |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| JP2943340B2 (en) * | 1991-01-24 | 1999-08-30 | 株式会社デンソー | Accumulator type fuel injection device |
| DE4414242A1 (en) * | 1994-04-23 | 1995-10-26 | Bosch Gmbh Robert | Fuel injection device for internal combustion engines |
| JP3918253B2 (en) * | 1997-09-10 | 2007-05-23 | 三菱ふそうトラック・バス株式会社 | Safety device for accumulator fuel injector |
| JPH11280930A (en) * | 1998-03-30 | 1999-10-15 | Denso Corp | Gas bleeding device |
| DE19822671A1 (en) * | 1998-05-20 | 1999-11-25 | Bosch Gmbh Robert | Pressure limiting valve for internal combustion engine |
| DE10114252C2 (en) * | 2001-03-22 | 2003-01-30 | Mtu Friedrichshafen Gmbh | Method for injecting fuel into the combustion chambers of an internal combustion engine, and fuel injection system for such |
| JP3555588B2 (en) * | 2001-03-23 | 2004-08-18 | トヨタ自動車株式会社 | Common rail fuel injector |
| FI117805B (en) * | 2003-06-17 | 2007-02-28 | Waertsilae Finland Oy | Arrangement in the fuel supply system |
| WO2007009279A1 (en) * | 2005-07-18 | 2007-01-25 | Ganser-Hydromag Ag | Accumulator injection system for an internal combustion engine |
| US7926745B2 (en) * | 2006-11-27 | 2011-04-19 | Mitsubishi Electric Corporation | Fuel injection valve |
| DE102007021085B4 (en) * | 2007-05-03 | 2009-01-15 | L'orange Gmbh | Injection system for with fuel, especially heavy oil, powered internal combustion engines |
-
2011
- 2011-06-10 DK DK11169400.6T patent/DK2423498T3/en active
- 2011-06-10 EP EP11169400.6A patent/EP2423498B1/en not_active Not-in-force
- 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
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN1985088A (en) * | 2004-07-30 | 2007-06-20 | 西门子公司 | Valve for use in a fuel line of a motor vehicle |
| DE102005012165A1 (en) * | 2005-03-17 | 2006-09-28 | L'orange Gmbh | Fuel storage for fuel injection system of internal combustion engine of motor vehicle, has segments, of which two are connected with remaining for supplying fuel over linking lines, if break or leakage occurs in one segment |
| WO2007014733A1 (en) * | 2005-08-02 | 2007-02-08 | L'orange Gmbh | Fuel injection system for an internal combustion engine |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103016426A (en) * | 2012-12-06 | 2013-04-03 | 联合汽车电子有限公司 | Jet pump nozzle integrating pressure relief valve |
| 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 |
| CN105264216A (en) * | 2013-06-12 | 2016-01-20 | Mtu腓特烈港有限责任公司 | Quantity-limiting valve |
| CN105264216B (en) * | 2013-06-12 | 2017-11-17 | Mtu 腓特烈港有限责任公司 | Meter valve |
| CN105626341A (en) * | 2014-11-21 | 2016-06-01 | Omt都灵机械车间有限公司 | A fuel flow limiting valve for large internal combustion engines |
| CN105626341B (en) * | 2014-11-21 | 2018-12-14 | Omt都灵机械车间有限公司 | Fuel flow rate for large combustion engines limits valve |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2423498B1 (en) | 2013-09-11 |
| KR101917389B1 (en) | 2018-11-09 |
| EP2423498A1 (en) | 2012-02-29 |
| JP5881981B2 (en) | 2016-03-09 |
| JP2012047170A (en) | 2012-03-08 |
| CN102383995B (en) | 2016-04-27 |
| KR20120020056A (en) | 2012-03-07 |
| DK2423498T3 (en) | 2013-12-09 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102383995A (en) | Passive flow control valve | |
| CN101578445B (en) | Injector for injecting fuel into combustion chambers of internal combustion engines | |
| US10378535B2 (en) | Damping assembly | |
| CN108138717B (en) | Fuel injector | |
| CN103370529A (en) | Fuel injection system | |
| CN100587252C (en) | Fluid pump having plunger and method of monoblock casting for housing of the same | |
| EP3516192B1 (en) | Dual fuel injector | |
| US20190293067A1 (en) | Cryogenic pump | |
| CN105443457A (en) | Continuous liquid pressurizing mechanism and liquid pressure producing method realized by using same | |
| CN108691705A (en) | fuel injection system for internal combustion engine | |
| CN101925734B (en) | Fuel injector | |
| CN102207051A (en) | Fuel injection device | |
| CN102734025B (en) | Fluid ejection apparatus | |
| CN206398122U (en) | A kind of new multistage noise reduction V-type ball valve | |
| US20160245251A1 (en) | Gas Metering Valve for a Dual Fuel Engine | |
| CN105626341B (en) | Fuel flow rate for large combustion engines limits valve | |
| CN206309679U (en) | Super high pressure fluid unloading valve | |
| CN107850010A (en) | Multi-plunger cryogenic pump with inlet manifold | |
| JP5715354B2 (en) | High voltage connection and connection configuration | |
| EP3017183A1 (en) | Distributed fuel injection equipment | |
| JP6866243B2 (en) | Fuel injection device | |
| CN208918729U (en) | High pressure common rail injector for diesel engine | |
| CN101598094B (en) | Direct control type shell deformation fluid injector for novel engine | |
| JP4566277B2 (en) | Large two-cycle diesel engine with exhaust valves that move outward | |
| CN201396230Y (en) | Direct control type housing deformation fluid jetting device used for engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20160427 Termination date: 20190825 |