CN101135283A - High-pressure fuel supply pump - Google Patents
High-pressure fuel supply pump Download PDFInfo
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- CN101135283A CN101135283A CNA2007101399023A CN200710139902A CN101135283A CN 101135283 A CN101135283 A CN 101135283A CN A2007101399023 A CNA2007101399023 A CN A2007101399023A CN 200710139902 A CN200710139902 A CN 200710139902A CN 101135283 A CN101135283 A CN 101135283A
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- 238000006731 degradation reaction Methods 0.000 claims description 10
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- 230000033228 biological regulation Effects 0.000 claims description 3
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Images
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
- F02M63/023—Means for varying pressure in common rails
- F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
- F02M63/0245—Means for varying pressure in common rails by bleeding fuel pressure between the high pressure pump and the common rail
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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
- F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
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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
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
- F02M59/367—Pump inlet valves of the check valve type being open when actuated
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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
- F02M59/462—Delivery 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
- 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
- F02M63/005—Pressure relief 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
- 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
- F02M63/0054—Check 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
- 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
- F02M63/0056—Throttling valves, e.g. having variable opening positions throttling the flow
-
- 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
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The present invention provides a high-pressure fuel supply pump, when ejecting value is open and under transient state of high-pressure fuel pump pressing fuel, even though the pressure of instant ejecting fuel increase to become abnormal pressure, the safety value will not be open. In the fuel ejecting path of upstream side (that is ejecting value side) of the safety value within the fuel safety path, setting a mechanism for preventing the pressure generated instantly within the path to enter the safety value. More specifically, setting alveolus in the safety path, which reduces the acting energy to the safety value of the pressure due to opening high-pressure fuel pump value; or setting mechanism for cutting off the transmission of anormal pressure in the safety path.
Description
Technical field
The present invention relates to the fuel of sending here from charging pump is pressurizeed, and with its be sent to internal-combustion engine Fuelinjection nozzle, especially for the high-pressure fuel feed pump of cylinder fuel injection type internal-combustion engine.
Relate in particular to a kind of high-pressure fuel feed pump of assembling safety valve (relief valve) mechanism on pump case, this relief valve mechanism is the safety valve as the abnormal pressure of the fuel pressure that is used to avoid the high pressure side fuel passage.
Background technique
Existing this high-pressure fuel feed pump, as disclosed in the TOHKEMY 2003-343395 communique, on the pump case of high-pressure fuel feed pump, be provided with the fuel security path of the low-pressure fuel path of the high pressure fuel passage that connects ejection valve downstream and suction valve upstream, be provided with as only being permitted the safety check of fuel from the logical safety valve of high pressure fuel passage one side direction low-pressure fuel path one effluent in the inside of this fuel security path.
Like this, when abnormal pressure appears in fuel under high pressure ejection path one side, open the safety valve that constitutes by this safety check, the part of fuel under high pressure is discharged to low-pressure passage one side, remove abnormal pressure.
Patent documentation 1: TOHKEMY 2003-343395 communique
, in the high-pressure fuel feed pump that constitutes like this, under the ejection transition state that valve is opened, high pressure fuel pump pressurizes to fuel, the pressure moment that produces ejection fuel surpasses the state of the cracking pressure of safety valve.
Because like this high pressure conditions of moment is not the abnormal state of system, so necessity that safety valve not have to move, be failure to actuate.
Safety valve under such situation open valve events, existing causes as the decline of the spray volume of high-pressure fuel feed pump and causes the problem of the decline of energy efficiency.
Summary of the invention
The present invention in view of this, purpose is under ejection valve is opened, high pressure fuel pump pressurizes to fuel transition state, even pressure moment of ejection fuel rises, safety valve is not opened yet.
Above-mentioned purpose is reached by following, that is: in the fuel ejection path of the upstream side by the safety valve in the fuel security path (promptly, ejection valve one side), the pressure that prevents moment of producing in this path is set rises and reach to mechanism that safety valve is propagated.
Specifically, reach by degradation of energy mechanism is set on security path, described degradation of energy mechanism make based on open at high pressure fuel pump valve events during the effect degradation of energy to safety valve of rising of the short-term pressure of ejection path one side that produces.
Preferably, degradation of energy mechanism can be made of near the plate that possesses at least one aperture of the high pressure fuel passage side setting safety valve.
Preferably, degradation of energy mechanism can constitute by the ejection valve of opening in the valve events that near the security path the safety valve upstream is carried out throttling or block.
The invention effect
The present invention according to such formation, producing under the situation of abnormal pressure because of fault of Fuelinjection nozzle etc., the fuel that is pressed into unusual high pressure is released by safety valve, the machine that can have pipe arrangement and other is because of the effect of abnormal pressure damaged, can provide simultaneously high compression rate, be the high high-pressure fuel feed pump of energy efficiency.
Moreover, not only be released to low-pressure passage by the d/d fuel of safety valve, also can be discharged into the pressurized chamber.
Description of drawings
Fig. 1 is the whole longitdinal cross-section diagram of the enforcement of the present invention first and second embodiment's high-pressure fuel feed pump;
Fig. 2 is a whole view in transverse section of implementing the high-pressure fuel feed pump of the first embodiment of the present invention;
Fig. 3 is an example that adopts the fuel supply system of the high-pressure fuel feed pump of implementing the first embodiment of the present invention;
Fig. 4 is interior each several part of the enforcement of the present invention first and second embodiment's high-pressure fuel feed pump and the pressure waveform in the common-rail;
Fig. 5 is an example implementing the aperture plate of the first embodiment of the present invention;
Fig. 6 is another example of implementing the aperture plate of the first embodiment of the present invention;
Fig. 7 is the schematic representation that the high pressure of the high-pressure fuel feed pump of the expression enforcement first embodiment of the present invention sprays the relation of flow and common-rail internal pressure;
Fig. 8 is the schematic representation of the structure of the expression relief valve mechanism of implementing the second embodiment of the present invention;
Fig. 9 is the longitdinal cross-section diagram under another angle of implementing the high-pressure fuel feed pump of the second embodiment of the present invention;
Figure 10 is a view in transverse section of implementing the high-pressure fuel feed pump of the second embodiment of the present invention;
Figure 11 is an example that adopts the fuel supply system of the high-pressure fuel feed pump of implementing the first embodiment of the present invention;
Figure 12 is the schematic representation of action of ejection valve system of schematically representing to implement the high-pressure fuel feed pump of the second embodiment of the present invention, and the expression high-pressure fuel feed pump is in the situation of ejection during the stage;
Figure 13 is the schematic representation of operating principle of ejection valve system of schematically representing to implement the high-pressure fuel feed pump of the second embodiment of the present invention, the situation when the expression high-pressure fuel feed pump is in unloaded state;
Figure 14 is the ssembly drawing of ejection valve system of implementing the high-pressure fuel feed pump of the second embodiment of the present invention;
Figure 15 is the schematic representation of structure of the ejection valve system of the expression high-pressure fuel feed pump of implementing the second embodiment of the present invention, and the expression high-pressure fuel feed pump is in the situation of ejection during the stage;
Figure 16 is the schematic representation of structure of the ejection valve system of the expression high-pressure fuel feed pump of implementing the second embodiment of the present invention, the situation when the expression high-pressure fuel feed pump is in sucting stage and returns the stage;
Figure 17 is the schematic representation of structure of ejection valve system of representing to implement the high-pressure fuel feed pump of the second embodiment of the present invention by vertical cross-section diagram and horizontal sectional view, and the expression high-pressure fuel feed pump is in the situation of ejection during the stage;
Figure 18 is the schematic representation of structure of ejection valve system of representing to implement the high-pressure fuel feed pump of the second embodiment of the present invention by vertical cross-section diagram and horizontal sectional view, the situation when the expression high-pressure fuel feed pump is in sucting stage and returns the stage.
Among the figure, 1-pump case; 2-plunger; 6-cylinder; 8-ejection valve system; 9-pressure pulsation reduces mechanism; 11-pressurized chamber; 30-electromagnetism suction valve mechanism; 200, B200-relief valve mechanism; 214-aperture plate; 210,211,215-suction path.
Embodiment
Below, specify embodiments of the invention with reference to accompanying drawing.
Based on Fig. 1 to Fig. 3, specify the first embodiment of the present invention.Structure and the action of at first using the overall structure figure of system shown in Figure 3 to come illustrative system.
Represented the pump case 1 of high-pressure service pump by the part of dotted line, the mechanism that represents in this dotted line, part are assembled in the pump case 1 of high-pressure service pump by one.
The fuel of fuel bath 20 is drawn up under the effect of charging pump 21, is sent to the suction attachment 10a of pump case 1 by suction pipe arrangement 28.At this moment, the suction fuel that flows to pump case 1 is adjusted to certain pressure at pressure governor 22 places.
The fuel that has passed through suction attachment 10a reduces mechanism 9, sucks the suction port 30a that path 10c, 10d arrive the electromagnetism suction valve mechanism 30 that constitutes volume-variable mechanism via pressure pulsation.The back describes pressure pulsation in detail and reduces mechanism 9.
Electromagnetism suction valve mechanism 30 possesses electromagnetic coil 30b, under the state of this electromagnetic coil 30b energising, to the state that the dextrad of Fig. 3 moves, keeps the state that spring 33 has been compressed with electromagnetic plunger 30c.
At this moment, the suction valve body of installing at the front end of electromagnetic plunger 30c 31 is opened the suction port 32 that links to each other with the pressurized chamber 11 of high-pressure service pump.
Under the cold state of electromagnetic coil 30b, and when between suction path 10d (suction port 30a) and pressurized chamber 11, not having fluid differential pressure, by the active force of this spring 33, suck valve body 31 quilts to closing the valve direction application of force, suction port 32 is in pent state.
The specific as follows action.
By the rotation of cam described later, plunger 2 be displaced to Fig. 1 below and when being in the sucting stage state, the capacity of pressurized chamber 11 increases, fuel pressures in the pressurized chamber 11 descend.If the fuel pressure in the pressurized chamber 11 becomes and is lower than the pressure that sucks path 10d (suction port 30a) in this stage, then sucking the valve opening force (making the power of valve body 31 that sucks) that the fluid pressure difference of valve body 31 places generation because of fuel produces to the right-hand displacement of Fig. 1.
By the valve opening force that produces because of this fluid pressure difference, suck valve body 31 and be designed to overcome the active force of spring 33 and drive valve, open suction port 32.
Under this state, as if the control signal that electromagnetism suction valve mechanism 30 is applied from control unit of engine 27 (to call ECU in the following text), then circulation has electric current in the electromagnetic coil 30b of electromagnetism suction valve mechanism 30, under the effect of magnetic force, electromagnetic plunger 30c moves to the dextrad of Fig. 1, keeps spring 33 compressed states.Its result keeps the state that valve body 31 has been opened suction port 32 that sucks.
Electromagnetism suction valve mechanism 30 is applied under the state of input voltage keeping, finish sucting stage at plunger 2, when carrying out the transition to compression stage, if plunger 2 is transferred to compression stage (state that moves to the top of Fig. 1), then owing to the "on" position of having kept to electromagnetic coil 30b, so still kept magnetic force, sucked valve body 31 and still be in out the valve state.
The capacity of pressurized chamber 11 reduces along with the ascending motion of plunger 2, but under this state, owing to, return to sucking path 10d (suction port 30a) by the suction valve body 31 of opening the valve state once more, so the pressure of pressurized chamber can not rise in case be inhaled into the fuel of pressurized chamber 11.This stage is called the stage of returning.
Under this state, remove control signal from ECU27, cut off energising to electromagnetic coil 30b, the magnetic force that acts on electromagnetic plunger 30c (magnetic, mechanicalness are after lag time) behind the certain hour by cancellation.Because effect has the active force of spring 33 on suction valve body 31, so, then suck valve body 31 and under the effect of the active force of spring 33, close suction port 32 if acting on the electromagnetic force of electromagnetic plunger 30c disappears.If suction port 32 is closed, then rise along with the ascending motion of plunger 2 from the fuel pressure that begins pressurized chamber 11 this moment.
And if 11 residual fuel are pressurized in the pressurized chamber, the fuel pressure of pressurized chamber 11 reaches more than the pressure of part of ejiction opening 12, then by ejection valve system 8, ejiction opening 12 to high press fit pipe 29 ejections, supply with to common-rail 23.This stage is called the ejection stage.That is to say that the compression stage of plunger 2 (from descending initial point to the ascent stage the last initial point) comprises the stage of returning and ejection stage.
Then, to the moment of the energising of the electromagnetic coil 30b of electromagnetism suction valve mechanism 30, can control the amount of the fuel under high pressure of ejection by the control releasing.Releasing was shifted to an earlier date to the moment of electromagnetic coil 30b energising, make the ratio in the stage of returning in the compression stage little, make the ratio in ejection stage big.
That is to say that turn back to the fuel that sucks path 10d (suction port 30a) and reduce, the fuel that is sprayed by high pressure increases.On the other hand,, make the ratio in the stage of returning in the compression stage become big, the ratio in ejection stage is diminished if the moment of removing input voltage is lagged behind.
That is, turn back to the fuel that sucks path 10d and become many, the fuel that is sprayed by high pressure tails off.Releasing is to be controlled by the instruction from ECU to the moment of the energising of electromagnetic coil 30b.
By forming above structure, remove to the moment of the energising of electromagnetic coil 30b by control, the amount of the fuel that is pressurized to high pressure and discharges can be controlled to the amount that internal-combustion engine needs.
Like this, be imported into the fuel of fuel suction attachment 10a, make necessary amount be pressed into high pressure by the to-and-fro motion of plunger 2, be pressed to common-rail 23 from ejiction opening 12 in the pressurized chamber 11 of pump case 1.
Sparger 24, pressure transducer 26 are installed on the common-rail 23.The number of cylinders that sparger 24 is matched with internal-combustion engine is mounted, and the control signal switch valve according to control unit of engine (ECU) 27 injects fuel in the cylinder.
Inlet in common-rail 23 is provided with throttle orifice 25, thus, blocks the propagation of pressure overshoot in common-rail 23, can be to the stable fuel of sparger 24 supply pressures.
On pump case 1, also be provided with downstream side that is communicated with ejection valve 8b and the security path 210,215 that sucks path 10c in addition.
Be provided with safety valve 202 on security path 210,215, flowing of these safety valve 202 fuel limitations only permitted to flow to a direction that sucks path 10c from the ejection path.Concrete structure is that the basis illustrates with Fig. 2.
Be pressed into fixedly emergency valve seat 201 at pump case 1, between pump case 1 and emergency valve seat 201 with the fixing aperture plate 214 of the form that sandwiches.Safety valve 202, is crushed on the emergency valve seat 201 under the effect of the pressing force of safety spring 204 by safe pressing member 203.The cracking pressure of safety valve 202 is to be determined by the pressing force that safety spring 204 produces, but this pressing force also can be determined as follows, promptly, make screw thread of carving at the periphery spiral shell of safety spring regulator 205 and the threads engaged of carving, determine by the decrement of adjusting safety spring 204 at pump case 1 spiral shell.Fuel encircles the fuel of 213 sealant flows to the outside by O.
Below describe with regard to the action of safety valve.Safety valve 202 is set at the safety spring 204 that produced pressing force by pressing to emergency valve seat 201, if in the suction chamber and the pressure difference between in the security path more than the pressure of regulation, then safety valve 202 leaves, opens valve from emergency valve seat 201.Aperture plate 214 is arranged in the way of security path 210, can not make safety valve 202 open sensitively because of the sudden turn of events of the pressure in the security path 210.
Because of the fault of sparger 24 etc. when common-rail 23 grades produce abnormal pressure; if the pressure reduction of security path 210 and suction path 10c is more than the cracking pressure of safety valve 202; then valve left by safety valve 202; the fuel that becomes abnormal pressure returns to sucking path 10c, high-voltage section pipe arrangements such as protection common-rail 23 from security path 210.
In first embodiment, ejection valve system 8, electromagnetism suction valve mechanism 30 are across pressurized chamber's 11 coaxial continuous configurations, and relief valve mechanism 200 is assembled in the safety valve mounting hole place that forms on the pump case concurrently with respect to the installation axis of ejection valve system 8, electromagnetism suction valve mechanism 30.
Below utilize Fig. 1, Fig. 2 to further describe fuel under high pressure pump structure, action.
Be formed with recess 1A as pressurized chamber 11 at pump case 1 center, from the inner circle wall of this pressurized chamber 11 to being formed with the recess 11A that is used to install ejection valve system 8 ejiction opening 12.And installing on the same axis of recess 11A of usefulness with the ejection valve system, be provided with hole 30A at the outer side wall of pump case, described hole 30A is used to install the electromagnetism suction valve mechanism 30 that uses to pressurized chamber's 11 fuelings.
With respect to central axis as the recess 1A of pressurized chamber 11, the axis that is used to that the recess 11A of ejection valve system 8 is installed and is used to install the hole 30A of electromagnetism suction valve mechanism 30 formation that intersects at a right angle respectively.
Be provided with and be used for 11 ejection valve systems 8 to ejection path ejection fuel from the pressurized chamber.
In addition, the cylinder 6 of the advance and retreat motion of guiding plunger 2 is installed in the face of pressurized chamber 11.
In first embodiment, the axis that is used to install the recess 11A of ejection valve system 8 and is used to install the hole 30A of electromagnetism suction valve mechanism 30 is formed on same axis, therefore, can directly be assembled into the recess 11A of the installation usefulness of ejection valve system 8 from the hole 30A that is used to install electromagnetism suction valve mechanism 30.Perhaps, can apply power when being pressed into ejection valve system 8 from the hole 30A that is used to install electromagnetism suction valve mechanism 30.At this moment, the diameter of hole 30A is necessary that in smallest diameter portion the maximum outside diameter that constitutes than ejection valve system 8 is big.
But the axis of these holes, recess can also stagger on circumferencial direction or above-below direction.
At this moment, ejection valve system 8 is from installing the opening 1B one side assembling of cylinder 6 usefulness.
The periphery of cylinder 6 is kept by cylinder seat 7, is screwed into spiral shell by the external screw thread that will be located at cylinder seat 7 peripheries quarter and is engraved in female thread on the pump case 1, and cylinder 6 is fixed on the pump case 1.Cylinder 6 remains on advance and retreat plunger movable 2 in the pressurized chamber 11, and plunger 2 can be slided along its advance and retreat moving direction.
In first embodiment, after will spraying valve system 8 and being installed in recess 11A, cylinder 6 is installed at the opening 1B place that is used to install cylinder 6.
Therefore, the front end of cylinder 6 can be inserted into the position of the inner end that regards to the ejection valve system of installing at recess 11A 8, thus, accommodate volume, so can improve the compression efficiency of fuel because can reduce the fuel of pressurized chamber 11.
In addition, in an embodiment, the end face of the opening 1B of the facial and pump case 1 of the flange shape ring-type that forms by periphery at cylinder 6 end face S1 is constituted metallic seal portion, with pressurized chamber 11 and isolated from atmosphere.Usually in high-pressure fuel feed pump, there is the worry that end face S1 is etched according to the cavitation that produces because of the pressure oscillation in the pressurized chamber 11, but so by cylinder 6 is projected in the pressurized chamber, thereby can make the sealing usefulness to the happening part of end face S1 away from cavitation, can reduce the erosion possibility.
In first embodiment, after ejection valve system 8 is installed, the interior week of the bottom (upper end portion among Fig. 1) by cylindrical member 11D being pressed into and being fixed to recess 1A, thus constitute the disconnecting prevention structure that sprays valve system 8.
This cylindrical member 11D also has the volume that reduces pressurized chamber 11, the function that improves the compression efficiency of fuel.Moreover, under the situation that cylindrical member 11D is not installed, can be used to cylinder 6 to spray the disconnecting prevention structure of valve system 8.
Under the situation that is provided with this cylindrical member 11D,,, constitute the position that does not reach ejection valve system 8 so can shorten the length of cylinder 6 because of there is no need a cylinder 6 as disconnecting prevention structure.
In addition, after ejection valve system 8 is pressed into recess 11A, for example the periphery of pressurized chamber's one side 11 is fastened on the inwall of pump case, can also disconnecting prevention structure be set certainly on one's body at ejection valve system 8.In this case, need cylindrical member 11D.In addition, if constitute the length that shortens cylinder 6, the position that does not reach ejection valve system 8, then all right first fixed cylinder 6 is installed in recess 11A place to ejection valve system 8 afterwards.
Be provided with push rod 3 in the lower end of plunger 2, the rotation motion of the cam 5 that described push rod 3 will be installed at the camshaft of motor is changed to and moves up and down, and passes to plunger 2.Plunger 2 is crimped on push rod 3 by stopper 15 by spring 4.Thus, along with rotatablely moving of cam 5, can make plunger 2 advance and retreat up and down (back and forth) motion.
In addition, be maintained at the plunger seal 13 of interior all underparts of cylinder seat 7, can with the state of the periphery sliding contact of plunger 2 under, be set at underpart among the figure of cylinder 6, prevent that fuel leak is to the outside.Prevent that simultaneously the lubricant oil (also comprising engine oil) that the slide part in the engine compartment is lubricated from flowing into the inside of pump case 1.
Be fixed with pressure pulsation at damper cover (damper cover) 14 places and reduce mechanism 9, described pressure pulsation reduces mechanism 9 makes the pressure pulsation that produces in pump reduce to involving of fuel distribution tube 28.
Damper cover 14 is fixed on pump case 1 place, is made up of 10a, 10b, 10c as the suction path of low-pressure passage.The pressure pulsation that the pressure pulsation that to-and-fro motion along with plunger 2 is produced in pump reduced to involving of fuel distribution tube 28 reduces mechanism 9, is made up of two groups of metal diaphragms (metal diaphragm) group body 9A, 9B.Metal diaphragm group body 9A, 9B separately with two metal diaphragms in its peripheral part welding joint, be injected with inert gas in inside.On pump case 1, be provided with damper shell (damper housing) 10B that constitutes a suction path part, in this damper shell 10B, taken in two groups of metal diaphragm group body 9A, 9B.Two groups of metal diaphragm group body 9A, 9B dispose supporting member 10A1,10A2 in the mode at the interval of mutual maintenance regulation at peripheral portion.Carve the screw thread of establishing by twisting the periphery that is combined in damper cover 14, sealing component 10D is pressed means of press seals, thereby the damper chamber is sealed at the thread groove 10c place that is provided with in interior week of damper shell 10B.Thus, in sucking path 10, distinguish the damper chamber, form pressure pulsation and reduce mechanism 9.Also guide the fuel of suction between damper cover 14 and metal diaphragm group body 9A, between metal diaphragm group body 9A, 9B by path 10E, effect has essentially identical pressure on four barrier films.
In addition, in this embodiment,, also can for example fix by welding full week in the P position though be damper cover 14 to be fixed on the pump case by screw fixed.In this case, because also can seal, so can not want first embodiment's sealing component 10D by welding.
In addition, in this case, because the power of fixing metal barrier film group body disappears, so the fixedly preferred design of metal diaphragm group body 9A, 9B becomes to be independent of the fixing of damper cover 14.
In addition, also can after screw fixed, weld.In this case, can not want sealing component, and the same clamping bolt of screw fixed that can utilize with present embodiment fixes metal diaphragm group body 9A, 9B.
Ejiction opening (ejection side line joint) 12 is formed on the pump case 1, the way of 12 the fuel passage from suction port 10a to ejiction opening, is formed with the pressurized chamber 11 that fuel is pressurizeed.11 inlet is provided with electromagnetism suction valve mechanism 30 in the pressurized chamber.Quilt is to the direction application of force of closing suction port under the effect of the inhalation valve spring 33 of suction valve body 31 in being arranged at electromagnetism suction valve mechanism 30.Electromagnetism suction valve mechanism 30 becomes the safety check of fuel limitation circulating direction thus.About concrete structure and the action as mentioned above.
Returning in the stage,, sucking path 10 generation pressure pulsations because of returning to the fuel that sucks path 10d.This pressure pulsation is absorbed attenuating by metal diaphragm group body 9A, the expansion of 9B, contraction.Return in the stage, fuel just refluxes by sucking pipe arrangement 28 a little from suction port l0a, and most of fuel is absorbed by the volume-variation of metal diaphragm group body 9A, 9B.
Get back to Fig. 2, security path 215 is connected and sucks on the path 10c.Therefore, the outlet of safety valve 202 is connected between pressure pulsation reduction mechanism 9 and the described suction valve 31.
On aperture plate 214, shown in Fig. 5,6, be provided with one or plural aperture.
Then, illustrate by high-pressure fuel feed pump normally with the situation of fuel high pressure force feed to common-rail 23.
From plunger 2 rises be in the compression stage, from returning the moment that the stage enters into the pressure period, generation pressure overshoot pressurized chamber 11 in and then.11 pressure overshoot that produce are propagated to security path 210, aperture plate 214 from ejiction opening 12 in the pressurized chamber.Propagate into the pressure overshoot of aperture plate 214, the propagation to security path 211 under the effect of aperture 214a, 214b, 214c is blocked, and the pressure overshoot at security path 211 places does not reach more than the cracking pressure of safety valve 201.Therefore, the pressure difference of the entrance and exit of safety valve can not arrive more than the cracking pressure of safety valve, and safety valve can misoperation, and the amount of the fuel that is sprayed by high pressure can not reduce yet.
In above pump structure, retaining member 8d as the ejection valve guard is chimeric by being pressed into gently on valve seat member 8a under the state of having put into ejection valve 8b, ejection valve spring 8c, as ejection valve system 8, be assembled on the pump case 1 by being pressed into from pressurized chamber's 11 1 sides.
Thus, can seek the raising of assembling.In addition, by between ejection valve system 8 and ejection tubing connection portion 12, connecting the fuel passage that arrives safety valve, can easily safety valve be built in the pump.
Pump case 1 is provided with the limited part of ejection valve system 8, and 11 sides are provided with the cylinder 6 of the abjunction preventing part that is provided with valve seat member 8a in the pressurized chamber, is provided with at valve seat member 8a and cylinder 6 and is pressed into the little gap of chimeric length than valve seat member 8a and pump case 1.
Thus, even what reduce valve seat member and pump case is pressed into inlay resultant force (being pressed into magnitude of interference), because valve seat member can not deviate from yet,, can prevent the distortion of the valve seat part when being pressed into and the deterioration of the valve seat performance that causes so there not be increase to be pressed into necessity of inlay resultant force (being pressed into magnitude of interference).Therefore, can manage the tolerance width that is pressed into inlay resultant force (being pressed into magnitude of interference) roughly, can cheap processing.
In addition, because it is gapped between valve seat member 8a and cylinder 6, so positional deviation that the tolerance of size of the various piece in the time of can absorbing by assembling by the gap causes, in addition, even valve seat member 8a moves with this gap value when pump moves, also can guarantee to be pressed into embedding part, therefore can keep the sealing of the portion of being pressed into.
In the present embodiment, be screwed into the internal diameter of the ejiction opening 12 of ejection side line joint, can be identical with the external diameter of the valve seat member 8a of the external diameter maximum of ejection valve system 8, maybe can be littler than it.Its result can reduce the area of the sealed department between ejiction opening and the joint, can access the effect of the compression area that can reduce sealed department.
The periphery of cylinder 6 is kept by cylinder seat 7.Cylinder seat 7 obtains thrust by the screw thread of carving at interior all spiral shells of flanged housing 40 is screwed in the pump case 1 spiral shell screw thread at quarter, and cylinder 6 is fixed on the pump case 1.The plunger 2 that cylinder 6 keeps as pressing element, and it can be slided up and down.
In addition, high-pressure fuel feed pump is fixing to motor, utilizes flanged housing 40 and flange 41 to carry out.Flanged housing 40 is fixed in motor by flange 41 screw 42 crimping that are fixed.Flanged housing 40 is because being engraved in the screw thread in interior week by spiral shell is fixed on the pump case 1, so pump case is fixed on the motor thus.
On aperture plate 214, be provided with one or more aperture.The example of expression aperture plate 214 in Fig. 5, Fig. 6.What Fig. 5 represented is the example that is provided with an aperture 214a.Fig. 6 is provided with four aperture 214b, further is provided with the example of a plurality of aperture 214c.In this case, a plurality of apertures are subjected to the viscous effects diameter of fuel more little more.Below, describe with regard to the function of this aperture.
At first, illustrate by high-pressure fuel feed pump normally with the situation of fuel high pressure force feed to common-rail 23.
High-pressure fuel feed pump produces pressure overshoot in pressurized chamber 11 in the ejection stage.11 pressure overshoot that produce are propagated to security path 210, aperture plate 214 from ejiction opening 12 in the pressurized chamber.Propagate into the pressure overshoot of aperture plate 214, under the effect of aperture 214a (214b, 214c), blocked propagation, thereby can reduce the pressure overshoot at security path 211 places to security path 211.Thus, safety valve can not carry out misoperation, can also reduce the slippage of the fuel that is sprayed by high pressure.That is to say, can keep the efficient of the high-pressure fuel feed pump of high level.
Moreover 11 pressure overshoot that produce are also propagated to common-rail 23 from high press fit pipe 29 through ejiction opening 12 in the pressurized chamber.Be provided with aperture 25 in the ingress of common-rail 23, thus, block the propagation of pressure overshoot in common-rail 23, can be to the stable fuel of sparger 24 supply pressures.
Secondly, illustrate because of the situation at the high-voltage section generation abnormal pressure of common-rail 23 grades such as the fault of sparger 24.
Fig. 7 represents the amount of the fuel that sprayed by high pressure from high-pressure fuel feed pump and the relation between the pressure in the common-rail 23.In general, even the cracking pressure of safety valve 202 is identical, the fuel that is sprayed by high pressure is many more, and the fuel pressure in the common-rail 23 is also necessarily high more.
On the other hand, then such as described if at the inlet of safety valve 202 aperture is set as shown in Figure 2 by aperture plate 214 grades, can reduce the misoperation of the safety valve 202 that causes because of the pressure overshoot that produces at path 210.But,, have to establish aperture 214a very for a short time in order to block the propagation of pressure overshoot to safety valve 202.Under the situation that has produced abnormal pressure, fuel under high pressure is returned to sucking path 10b from security path 215 by this aperture 214a, but because of producing the pressure loss at aperture 214a, become and be far longer than the cracking pressure of safety valve 202 so the result is a fuel pressure in common-rail 23 grades.Resistance to pressure, the cost of therefore high press fit pipe portion become problem.
On the other hand, as shown in Figure 6,, then can block the propagation of pressure overshoot, and when abnormal pressure produces, can suppress the rising of the pressure of common-rail 23 grades to safety valve 202 if a plurality of more little aperture 214b, 214c of viscous effects that are subjected to fuel more are set.Though the area of passage of one by one aperture 214b, 214c is little, their the total area of passage can be enough big, and this is because can not produce the pressure loss at aperture 214b, 214c.Therefore, can avoid the resistance to pressure and the cost problem of high press fit pipe portion.
In addition, become the fuel of abnormal pressure,,, therefore in sucking path 10b, produce very large pressure pulsation because fuel pressure sharply reduces when sucking path 10b release.But, on suction path 10b, be provided with pressure pulsation and reduce mechanism 9, can fully lower this pressure pulsation thus, so can prevent the propagation of pressure pulsation, prevent the breakage of pipe arrangement to low-pressure fitting pipe 28.
In addition, even replace aperture plate 214, setting has the sintering metal of mesh structure etc., also can obtain identical effect.
Moreover, in this embodiment, the situation that the outlet of security path is connected in suction (low pressure) path has been described, but also can be arranged on safety valve the position of approaching the pressurized chamber, preferably be arranged in the pressurized chamber, compression efficiency only otherwise reduce and just can be connected in the pressurized chamber to the outlet of security path can also make fuel return the pressurized chamber when abnormal pressure.
Then, according to Fig. 1 and Fig. 8～Figure 18 second embodiment is described.
At first, describe with regard to the concrete structure of relief valve mechanism B200 with Fig. 8～Figure 10.
Relief valve mechanism B200 is by constituting as the bottom, that is: and Safety valve body B206, safety valve B202, safe pressing member B203, safety spring B204 and the safety spring regulator B205 of emergency valve seat B201 one.Relief valve mechanism B200 in the assembling of the outside of pump case 1, is fixed in pump case 1 by being pressed into as accessory part afterwards.
At first, in Safety valve body B206, insert in turn, safety spring regulator B205 is pressed into is fixed to Safety valve body B206 according to the order of safety valve B202, safe pressing member B203, safety spring B204.By the fixed position of this safety spring regulator B205, determine the load that is provided with of safety spring B204.The cracking pressure of safety valve B202 is determined according to the load that is provided with of this safety spring B204.The relief valve mechanism B200 that forms like this is pressed into is fixed in pump case 1.In a second embodiment, security path 211 is integrally formed at pump case 1 concurrently with respect to cylinder 6.
Then, utilize Figure 11, Figure 12, Fig. 13 that the function of ejection valve system 8 is described.11 outlet is provided with ejection valve system 8 in the pressurized chamber.Ejection valve system 8 is made up of ejection valve seat 8a, ejection valve 8b, ejection valve spring 8c and ejection valve seat 8d, ejection valve 8b keeps by ejection valve seat 8d and can slide, ejection valve 8b is when driving valve repeatedly and close the valve motion, by ejection valve seat 8d guiding, make ejection valve 8b only on stroke direction, move.In addition, ejection valve 8b contacts with the contacting part 8d3 of ejection valve seat 8d when driving valve, and action is limited.Like this, by the delay of closing of ejection valve 8b, the high pressure ejection can not be back in the pressurized chamber 11 to the fuel of ejiction opening 12 again, and the efficient of high-pressure service pump can not reduce.
In ejection valve seat 8d upper shed ejiction opening 8d1 and relief port 8d2, return port 8d4 are arranged.Relief port 8d2 and security path 211 are connected.Be in ejection during the stage at high-pressure fuel feed pump, as shown in figure 12, ejection valve 8b is in out the valve state.Ejection valve 8b contacts at contacting part 8d3 with spraying valve seat 8d, by this part fuel is sealed, so ejiction opening 12 and security path 211 are blocked, becomes and is not communicated with.
On the other hand, when high-pressure fuel feed pump was in suction and returns the stage, as shown in figure 13, ejection valve 8b was in the valve state that closes.Ejection valve 8b blocks ejection path 12 and pressurized chamber 11 by the seat portion 8a3 on the ejection valve seat 8a.Therefore, even the motion of the pressure in the pressurized chamber 11 by plunger 2 becomes low pressure, the fuel under high pressure in the ejection path 12 can not reflux to pressurized chamber 11 yet.In addition, at contacting part 8d3, the gap that produces the stroke size that just sprays valve 8b between ejection valve 8b and ejection valve seat 8d is communicated with ejiction opening 12 and security path 211 by this gap.That is to say, ejection during the stage ejiction opening 12 and security path 211 are non-connections, sucting stage and when returning the stage, ejiction opening 12 and security path 211 are communicated with.
Then, just normally the situation of fuel high pressure force feed to common-rail 23 described by high-pressure fuel feed pump.
During the ejection stage, 11 fuel that are pressed into high pressure in the pressurized chamber as shown in figure 12, are supplied with to common-rail 23 by high press fit pipe 29 by ejiction opening 12.
At this moment, in pressurized chamber 11, produce pressure overshoot.11 pressure overshoot that produce pass to ejiction opening 12 and go in the pressurized chamber, are in out the valve state but spray valve 8b this moment.That is to say, as mentioned above, because of ejiction opening 12 and security path 211 are non-connections, so this pressure overshoot can not propagate into security path 211.
Therefore, even 11 produce pressure overshoot in the pressurized chamber, safety valve B202 can misoperation yet.This means from the flow of high-pressure fuel feed pump and can not descend to common-rail 23 ejections.
On the other hand, at sucting stage and when returning the stage, though ejiction opening 12 and security path 211 be communicated with because there is not pressure overshoot, so safety valve B202 can misoperation.That is to say, can not descend from the flow of high-pressure fuel feed pump to common-rail 23 ejections.
And, just describe in the situation that high-voltage section such as common-rail 23 have produced abnormal pressure because of fault of sparger 24 etc.
During the stage, as mentioned above, are non-connections because of spraying path 12 and security path 211 in ejection, can not arrive safety valve B202 so become the fuel of abnormal pressure.
At sucting stage and when returning the stage, as mentioned above, ejiction opening 12 and security path 211 are communicated with.
Therefore, the fuel that has become abnormal pressure passes through security path 211 arrival safety valve B202 from ejiction opening 12.Then, passed through the fuel of safety valve B202, promptly sucked path 10b by the vent pathway B205a that opens at safety spring regulator B205 to low voltage section and discharge.Thus, the high-voltage section of protection common-rail 23 grades.
In addition, at the fuel that becomes abnormal pressure to sucking path 10b when discharging, because fuel pressure sharply descends, so in sucking path 10b, produce very large pressure pulsation thus.But, also be provided with pressure pulsation in the upstream that sucks path 10b and reduce mechanism 9, because this pressure pulsation can fully reduce,, can prevent the breakage of pipe arrangement thus so can prevent the propagation of pressure pulsation to low-pressure fitting pipe 28.
Secondly, the structure of the ejection valve system 8 that utilizes Figure 14, Figure 15, Figure 16, Figure 17, Figure 18 to illustrate to have above-mentioned functions.
The ejection valve system 8 that constitutes like this is pressed into is fixed on the pump case.Pressing part is that the side that the side face of ejection valve seat 8a promptly is pressed into 8a2 of portion and ejection valve seat 8d promptly is pressed into the 8d5 of portion.The side of ejection valve seat 8d is the shape that cuts out two parallel plane 8d6 on drum.That is to say that the side of ejection valve seat 8d is pressed into the 8d5 of portion and planar surface portion 8d6 forms by columnar.
Two ejiction opening 8d1 process in order to connect these two planar surface portion 8d6.Two relief port 8d2 columnarly to be pressed into the 8d5 of portion and to process in order to be connected in.Like this, an ejection valve system 8 when being pressed into pump case 1, be pressed into be fixed into the relief port 8d2 that on ejection valve seat 8d, processes and on pump case 1 security path 211 of processing overlapping.And the portion of being pressed into of pump case is processed to drum.
When discharging the stage, as Figure 15 and shown in Figure 17,11 pressurized fuel, are ejected to ejiction opening 12 by in the planar surface portion 8d6 of the side processing of ejection valve seat 8d and the gap between the pump case 1 from ejiction opening 8d1 in the pressurized chamber.At this moment, security path 211 and ejection path 12 are ejected contacting part 8d3 on the valve seat 8d and block and become non-connection.Thereby the pressure overshoot that produces in pressurized chamber 11 can not propagated to safety valve B202.
In addition, producing under the situation of abnormal pressure in high-voltage section such as common-rail 23 because of the fault of sparger 24 etc., as Figure 16 and shown in Figure 180, at contacting part 8d3 place, the gap that between ejection valve 8b and ejection valve seat 8d, produces the stroke size of ejection valve 8b, by this gap, ejiction opening 12 and security path 211 are connected via the connecting port 8d4, the relief port 8d2 that are provided with on ejection valve seat 8d.
Therefore, the fuel that has become abnormal pressure can arrive safety valve B202, promptly sucks path 10b by the vent pathway B205a that opens at safety spring regulator B205 to low voltage section and discharges.
In addition, be pressed into portion 8d5 and the ejection valve seat 8a3 of the ejection valve system 8 of assembling by ejection valve seat 8d is pressed into and is fixed between the pump case 1 outside pump case 1.Particularly the portion of being pressed into of 8d5 and pump case 1 becomes the structure that blocks between ejection path 12 and the security path 211 thus.
Also this can be pressed into and be made as the viscous effects that is subjected to fuel more between 8d5 of portion and the pump case 1 and more little aperture.Thus, obtain the effect identical, can reduce the load that is pressed into of 8 pairs of pump cases 1 of ejection valve system simultaneously, improve the assembling of high-pressure fuel feed pump with above-mentioned effect.
Industrial applicibility
The present invention is applicable to the high-pressure fuel feed pump that the internal-combustion engine of in-cylinder injection type adopts.In an embodiment, just have only the so-called single cylinder type high-pressure fuel feed pump of a pressurized chamber to be illustrated, but also can be used to have the pump of so-called many cylinder types of a plurality of pressurized chambers.
Claims (14)
1. high-pressure fuel feed pump, it is provided with the fuel security path, described fuel security path connects the high pressure fuel passage in the ejection valve downstream that is ejected in the fuel that has pressurizeed the pressurized chamber and the low-pressure fuel path or the described pressurized chamber of suction valve upstream, be provided with safety check as safety valve in this fuel security path inside, described safety check is only permitted fuel and is led to described low-pressure fuel path or described pressurized chamber side from the high pressure fuel passage effluent
Described high-pressure fuel feed pump is characterised in that,
Be provided with pressure propagation in the fuel of the described ejection valve side of the described safety valve upstream in the described fuel security path ejection path and prevent mechanism, described pressure propagation prevents mechanism to prevent the propagation of the pressure rising of moment of producing to described safety valve in this ejection path.
2. high-pressure fuel feed pump as claimed in claim 1 is characterized in that,
Be provided with degradation of energy mechanism on described security path, described degradation of energy mechanism makes the degradation of energy of rising based on to the pressure of described safety valve in the described ejection path that described safety valve is opened act on the direction during described ejection valve is opened valve events.
3. high-pressure fuel feed pump as claimed in claim 2 is characterized in that,
Described degradation of energy mechanism constitutes: the plate with at least one aperture that is included near the high pressure fuel passage side setting the described safety valve.
4. high-pressure fuel feed pump as claimed in claim 2 is characterized in that,
Described degradation of energy mechanism comprises described ejection valve, drives ejection valve in the valve events by this and makes near the high pressure fuel passage throttling the described safety valve or block.
5. high-pressure fuel feed pump,
It has: the low pressure that sucks fuel to the pressurized chamber sucks path and sprays the ejection path of described fuel from described pressurized chamber,
Possess suction valve, possess the ejection valve at described suction path at described ejection path,
Also has security path, described security path connect described ejection path described ejection valve downstream side and the described suction valve of described suction path upstream side or be connected the downstream side and the described pressurized chamber of described ejection valve, and be the upstream, be the downstream or be the upstream, be the downstream with described pressurized chamber side with described ejection passage side with described suction passage side with described ejection passage side
In described security path, have safety valve, described safety valve fuel limitation only flow from upstream side downstream side one direction flow,
Described safety valve is formed in if the pressure difference between the entrance and exit reaches the cracking pressure of regulation and then drives valve when above,
Described high-pressure fuel feed pump is characterised in that,
The upstream side of the described safety valve in described security path is provided with pressure pulsation and removes mechanism, and described pressure pulsation is removed mechanism and made described pressure pulsation decay, and the pressure pulsation that perhaps prevents to produce in described ejection path is to described safety valve effect.
6. high-pressure fuel feed pump as claimed in claim 5 is characterized in that,
Remove mechanism as described pressure pulsation, near the described safety valve of described security path, be provided with aperture.
7. high-pressure fuel feed pump as claimed in claim 5 is characterized in that,
Remove mechanism as described pressure pulsation, near the described safety valve of described security path, be provided with a plurality of apertures side by side.
8. high-pressure fuel feed pump as claimed in claim 5 is characterized in that,
Remove mechanism as described pressure pulsation, be attached with the member of mesh configuration at the described safety valve of described security path.
9. high-pressure fuel feed pump as claimed in claim 5 is characterized in that,
Remove mechanism as described pressure pulsation, be provided with near the described safety valve of described security path the connection between described security path and the described ejection path, channel opening and closing mechanism that non-connection is switched.
10. high-pressure fuel feed pump as claimed in claim 9 is characterized in that,
Described channel opening and closing mechanism is constituted as and comprises following switching mechanism, described switching mechanism makes described security path and the non-connection of described ejection path in during described high-pressure fuel feed pump is in the ejection stage of fuel under high pressure, and described security path and described ejection path are communicated with.
11. high-pressure fuel feed pump as claimed in claim 10 is characterized in that,
Use described ejection valve as described channel opening and closing mechanism, this ejection valve open valve events the time by described ejection valve, make the joint throttling of described ejection path and described security path or block.
12. high-pressure fuel feed pump as claimed in claim 11 is characterized in that,
In the side of reciprocating tubular retaining member of the described ejection valve of guiding, be formed with the connection opening portion of described security path and described ejection path, when described ejection valve is driven valve, make described connection opening portion's throttling or block by this ejection valve.
13. high-pressure fuel feed pump as claimed in claim 12 is characterized in that,
Side at described tubular retaining member is provided with guiding path, and described guiding path is used for opening valve events with the fuel of the described pressurized chamber described ejection path that leads at described ejection valve.
14. high-pressure fuel feed pump as claimed in claim 12 is characterized in that,
Described tubular retaining member is fixed in the ejection opening portion of described pressurized chamber, valve seat member in that side fixing described ejection valve in the pressurized chamber of this tubular retaining member is used is pressed into this seat portion by the spring that is maintained at described tubular retaining member inside with described ejection valve.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006235866 | 2006-08-31 | ||
| JP2006235866A JP2008057451A (en) | 2006-08-31 | 2006-08-31 | High-pressure fuel supply pump |
| JP2006-235866 | 2006-08-31 |
Publications (2)
| Publication Number | Publication Date |
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| CN101135283A true CN101135283A (en) | 2008-03-05 |
| CN101135283B CN101135283B (en) | 2010-06-16 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007101399023A Active CN101135283B (en) | 2006-08-31 | 2007-08-03 | High-pressure fuel supply pump |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20080056914A1 (en) |
| EP (2) | EP1898084B1 (en) |
| JP (1) | JP2008057451A (en) |
| CN (1) | CN101135283B (en) |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN101135283B (en) | 2010-06-16 |
| EP1898084A1 (en) | 2008-03-12 |
| US20080056914A1 (en) | 2008-03-06 |
| EP1898084B1 (en) | 2013-01-09 |
| EP2336545B1 (en) | 2013-07-31 |
| JP2008057451A (en) | 2008-03-13 |
| EP2336545A1 (en) | 2011-06-22 |
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