CN101676548B - Fuel injection apparatus - Google Patents
Fuel injection apparatus Download PDFInfo
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- CN101676548B CN101676548B CN2009101707396A CN200910170739A CN101676548B CN 101676548 B CN101676548 B CN 101676548B CN 2009101707396 A CN2009101707396 A CN 2009101707396A CN 200910170739 A CN200910170739 A CN 200910170739A CN 101676548 B CN101676548 B CN 101676548B
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Abstract
A fuel-injection apparatus is composed of a console cabinet having a first console cabinet (51) and a second console cabinet (52), wherein the first and the second console cabinets (51, 52) are communicated by adjusting a throttle flow path (61) under a condition that the fuel pressure of the console cabinet is low relatively. The flow of fuel from the first console cabinet (51) to the second console cabinet (52) is restrained, thus there is a pressure difference between the first and the second console cabinets (51, 52). When a discharging hole (56) is closed, the pressure of the first console cabinet (51) is identical to that of the second console cabinet (52), however the fuel pressure of the first console cabinet (51) is altered in a high state relative to that of the second console cabinet (52) by adjusting the throttle flow path (61), thus it is possible to shorten a period from closing the discharging hole (56) until the valve member reaches a prescribed position (close position).
Description
Technical field
The present invention relates to a kind of hydraulically powered fuel injection system.
Background technique
In the past, the known fuel supply system that fuel is supplied to the sparger of the injection apparatus that acts as a fuel from high-pressure service pump.Be used for the sparger of this system, having the sparger that makes the hydraulic drive type that the valve member that is made of needle-valve etc. promotes by fuel pressure.As this sparger, for example disclose instruction piston (command piston) and the needle-valve that to constitute valve member and remain the sparger (for example with reference to patent documentation 1) that one forms.
Yet, in patent documentation 1 disclosed sparger, by the activity that comes the control valve parts in the fuel pressure in the control room of the opposition side of spray orifice configuration.Specifically, control control valve by the ECU equal controller, so that allow fuel when discharge in the control room, the fuel pressure in control room descends when control valve is driven valve.Thus, valve member is opened to control room side shifting, spray orifice, and burner oil.On the other hand, when control valve is closed valve in case fuel limitation when discharge in the control room, the fuel pressure in control room rises.Thus, valve member is closed to spray orifice side shifting, spray orifice, and stops the injection of fuel.
Patent documentation 1: Japanese kokai publication hei 9-32681 communique
But, when the sealing of spray orifice is observed, begin to the time that needs till the fuel pressure in control room rises to a certain degree from control valve being closed valve, therefore there be the time elongated problem of spray orifice before being closed.That is, to begin to move the needed time to valve member to assigned position elongated discharging from restriction from the fuel in control room.
Summary of the invention
The present invention carries out in order to address the above problem, and its objective is provides a kind of fuel injection system, and the fuel discharge that can shorten from restriction from the control room began to the time of valve member till assigned position moves.
In the fuel injection system shown in the 1st example, outer cover formation portion is that the 1st control room is supported and formed to valve member.The 1st control room makes valve member to moving axially by the fuel pressure of inside.And board forms the 2nd control room to the 1st control room opening.When the fuel pressure in the 1st and the 2nd control room descended, valve member and this board butt were so that the sealing opening.
And fuel injection system has supply side throttling stream and discharges side throttling stream.Supply side throttling stream is to be used for the stream supplied with to the 1st control room via throttling from the fuel of inlet side.On the other hand, discharging side throttling stream is the stream that fuel is discharged to outlet side via throttling from the 2nd control room.
Here, particularly in fuel injection system, possess pressure regulation throttling stream, this pressure regulation throttling stream is used for the fuel from inlet side is supplied to above-mentioned the 2nd control room via throttling, and the fuel pressure in above-mentioned the 1st control room is maintained fuel pressure height than above-mentioned the 2nd control room.And, under the state of above-mentioned valve member and above-mentioned board butt, flow to the fuel in above-mentioned the 2nd control room from above-mentioned the 1st control room and to be blocked, and only by above-mentioned pressure regulation throttling stream to the fuel of above-mentioned the 2nd control room supply from inlet side.
Promptly constitute, constitute the control room, under the low relatively state of the fuel pressure in control room, flow to the fuel in the 2nd control room from the 1st control room and to be blocked by the 1st control room and the 2nd control room.
Thus, if relatively reduce the flow path area etc. of pressure regulation throttling stream, suitably set the flow path area of pressure regulation throttling stream, then the fuel pressure in the 1st control room rises, and the fuel pressure in the 2nd control room descends on the other hand.If restriction is discharged from the fuel in the 2nd control room under this state, then the fuel pressure in the 2nd control room rises, and the fuel pressure in the 1st control room changes under high relatively state.Afterwards, the pressure in the 1st control room and the 2nd control room becomes identical, but the pressure ratio of this moment was high in the past.Thus, can make valve member move required fuel pressure reaching, can shorten fuel and discharge and begin to the time of valve member till assigned position moves from restriction from the control room than the Zao in the past moment.
So, when sealing the opening in the 2nd control room by valve member, the fuel pressure in the 1st control room also rises.On the other hand, in the 2nd control room, from pressure regulation throttling stream fueling, therefore, if relatively reduce the flow path area etc. of pressure regulation throttling stream, suitably set the flow path area of pressure regulation throttling stream, then the fuel pressure in the 2nd control room descends.And identical with above-mentioned formation, if restriction is discharged from the fuel in the 2nd control room under this state, then the pressure in the 2nd control room rises, and the pressure in the 1st control room changes under high relatively state.Afterwards, the pressure in the 1st control room and the 2nd control room becomes identical, but the pressure ratio of this moment was high in the past.Thus, can make valve member move required fuel pressure reaching, can shorten fuel and discharge and begin to the time of valve member till assigned position moves from restriction from the control room than the Zao in the past moment.
In addition, shown in the 2nd example, the pressure regulation throttling stream under this situation also can form the fuel passage of board inside of valve member butt and the intercommunicating pore in the 2nd control room.
Description of drawings
Fig. 1 is the summary pie graph of the fuel injection system of expression embodiment of the present invention.
Fig. 2 is the summary pie graph of the fuel injection system of expression embodiment of the present invention.
Fig. 3 is the local amplification sectional view that the feature of expression sparger constitutes.
Fig. 4 is the explanatory drawing that is used to illustrate the characteristic of sparger.
Fig. 5 is the explanatory drawing of the fuel path constructed according to the position of valve member of expression.
Fig. 6 is the explanatory drawing of the movement in time of expression fuel injection system.
Fig. 7 is the local amplification sectional view that the feature of expression sparger constitutes.
Fig. 8 is the local amplification sectional view that the feature of expression sparger constitutes.
Fig. 9 is the local amplification sectional view that the feature of expression sparger constitutes.
Figure 10 is the explanatory drawing of the fuel path constructed according to the position of valve member of expression.
Embodiment
Below, embodiments of the present invention are described with reference to the accompanying drawings.
(the 1st mode of execution)
The fuel injection system 1 of present embodiment shown in Figure 1 is the system that is used for to each cylinder injection fuel of internal-combustion engine, is to use the DME ejecting system of dimethyl ether (Dimethyl ether, abbreviation DME) as its fuel.
This fuel injection system 1 comprises the sparger 10 as " fuel injection system ", also has fuel tank 100, the supply pump 110 as low pressure pump, high-pressure service pump 120, high-pressure common rail 130, electric control device (hereinafter referred to as " ECU ") 140 etc. except sparger 10.
In fuel tank 100, store the DME that acts as a fuel with liquid condition.Supply pump 110 is extracted this fuel out.Supply pump 110 is connected with high-pressure service pump 120, and the fuel of being extracted out by supply pump 110 becomes fuel under high pressure by high-pressure service pump 120, and is accumulated in the high-pressure common rail 130.
High-pressure common rail 130 has supplying mouth 131 and a plurality of (being 6 in the present embodiment) exhaust port 132 of arranging on its length direction.High-pressure service pump 120 is connected with supplying mouth 131, and fuel under high pressure supplies in the high-pressure common rail 130 from this supplying mouth 131.On the other hand, be connected with sparger 10 respectively at a plurality of exhaust ports 132.Each sparger 10 is configured in each cylinder.Therefore, exhaust port 132 is provided with the quantity of the cylinder number of internal-combustion engine.In addition, in Fig. 1, only represent 1 sparger 10, other omissions.
And high-pressure common rail 130 has common rail pressure sensor 133, and the information relevant with the fuel pressure of high-pressure common rail 130 is transfused to ECU140.And high-pressure common rail 130 has reduction valve 134.This reduction valve 134 is controlled from the information of high-pressure common rail sensor 133 by the ECU140 basis.In addition, in Fig. 1 for fear of loaded down with trivial details and not shown from ECU140 to the reduction valve 134 guide line.Here, when valve left by reduction valve 134 by ECU140, the part of the fuel of being accumulated turned back to fuel tank 100, and the fuel pressure of high-pressure common rail 130 inside reduces.
ECU140 is to control the reduction valve 134 of high-pressure common rail 130 as described above, and when the internal pressure of high-pressure common rail 130 becomes constant pressure, carry out the energising to sparger 10, the fuel injection of control sparger 10.
Present embodiment is characterised in that the structure of this sparger 10.Next therefore, the structure of sparger 10 be described according to Fig. 2.Sparger 10 is, have as the parts that form its outer cover shell 13, valve body 14, every the joint sealing 15 between shell 13 and valve body 14 and from the outside locking nut 16 that these parts are fastening.In addition, shell 13, valve body 14, joint sealing 15 and locking nut 16 constitute " outer cover formation portion ".
Be provided with the spray orifice (not shown among Fig. 2) of burner oil at the front end of valve body 14.At these valve body 14 inner paths 20 that form, at the joint sealing 15 inner paths 21 that form.With being linked in sequence of path 18, path 21, path 20, fuel is directed into the front end of valve body 14 to these paths thus from inlet side.Below, valve body 14 1 sides suitably are designated as " forward end " of sparger 10.
And sparger 10 has the valve member 22 of accommodating in inside along its length direction.This valve member 22 begins to be made of pin 23, coupling part 24, instruction piston 25 from forward end.Pin 23 and instruction piston 25 are retained as one by coupling part 24.
And sparger 10 has solenoid valve portion 30 at the opposition side (following suitably be designated as " terminal side ") of forward end.Solenoid valve portion 30 links with respect to shell 13 by nut 31.Solenoid valve portion 30 is that the control valve 37 of T word shape etc. constitutes by terminal 32, armature 33, main body 34, cup type link stopper 35, coil 36, cross section.
On the basis of the basic comprising of above-mentioned explanation, below the multiple hydraulic control of explanation constitutes.
The hydraulic pressure of the 1st mode of execution constitutes as shown in Figure 3.Fig. 3 is the local amplification sectional view of part shown in the mark A among Fig. 2.
Between control valve 37 and instruction piston 25, be provided with orifice plate 41.Control valve 37 is illustrated by the situation of spring 38 (with reference to Fig. 2) application of force before, by the power that applies of spring 38, control valve 37 and orifice plate 41 butts.In detail, control valve 37 has valve 37a at its abutting part.Valve 37a is that the part with spheroid constitutes plane and constitutes.This orifice plate 41 limits around axial rotation by locating stud 42.In addition, orifice plate 41 constitutes " board ".
Next, further describe the formation of the hydraulic control of sparger 10.At first, orifice plate 41 has recess 43 in its underpart.The instruction piston 25 base end part can with these recess 43 butts.The instruction piston 25 base end part near become the less minor diameter part 25a of diameter, the 1st control room 51 be formed on this minor diameter part 25a around.And, be formed with the 2nd control room 52 cylindraceous in the part of the central shaft that comprises orifice plate 41.The 2nd control room 52 is to the 1st control room 51 (recess 43) opening.
Via the paths 17,19 that form in shell 13 inside and at the orifice plate 41 inner paths 53,54 that form, to the 1st control room 51 fuelings.Here, be formed with hand-hole 55, be communicated with 2 paths 53,54 by this hand-hole 55 in orifice plate 41 inside.Hand-hole 55 plays the effect of supply side throttling.In this sense, hand-hole 55 constitutes " supply side throttling stream ".
On the other hand, when the excitation attraction force of control valve 37 by coil 36 when terminal side moves, the fuel in the 2nd control room 52, via portal 56, at main body 34 inner fuel chambers 57, paths 58 that are connected with fuel chambers 57 that form and the path 59 that is connected with path 58, finally spill from exporting 12.On the other hand, during with orifice plate 14 butts, portal 56 by valve 37a sealing by the power that applies of spring 38 at control valve 37, fuel is not discharged from.Portal and 56 play the effect of discharging the side throttling.In this sense, portal and 56 constitute " discharging side throttling stream ".
Here, particularly shown in Fig. 4 (a), moved under the state (the not state of Ti Shenging) of forward end at instruction piston 25, because the 2nd control room 52 is to the 1st control room 51 (recess 43) opening, so work as 1 control room in the 1st control room 51 and the 2nd control room 52.That is, under the state that instruction piston 25 does not promote, pressure regulation throttling stream 61 is inoperative.Fig. 5 (a) schematically expresses this form.That is, shown in Fig. 5 (a), construct following path (path shown in the arrow A): path 53 → hand-hole 55 → control room 51, the 52 → 56 → fuel chambers 57 of portalling.
On the other hand, shown in Fig. 4 (b), moved under the state (state of lifting) of terminal side at instruction piston 25, the base end part of instruction piston 25 and recess 43 butts of orifice plate 41 are so that seal the opening in the 2nd control room 52.At this moment, path 54 and the 2nd control room 52 are communicated with by pressure regulation throttling stream 61.That is, under the state that instruction piston 25 has promoted, the 1st control room 51 and the 2nd control room 52 are by 61 connections of pressure regulation throttling stream.Fig. 5 (b) schematically expresses this form.That is, shown in Fig. 5 (b), construct following path (path shown in the arrow B): path 53 → hand-hole 55 → control room 51 → pressure regulation throttling stream 61 → the 2nd control rooms 52 → 56 → fuel chambers 57 of portalling.Pressure regulation throttling stream 61 herein constitutes " pressure regulation throttling stream ".
Next, the action to sparger 10 describes.Here, describe with reference to Fig. 4～Fig. 6.In addition, Fig. 6 is the explanatory drawing of the movement in time of expression each several part.At first, not by ECU140 to coil 36 (with reference to Fig. 2) when switching on, the valve 37a of control valve 37 and orifice plate 41 butts, and sealing portals 56.
Under this state, when by ECU140 during to coil 36 energising (moment t1 among Fig. 6), by the excitation attraction force of coil 36, the valve 37a of control valve 37 leaves (with reference to " the valve movement " Fig. 6) from orifice plate 41.So, portal 56 by open, the 2nd control room 52 56 is communicated with the fuel chambers 57 of low voltage side via portalling.Here, because that 56 the flow path area of portalling is set than hand-hole 55 is big, therefore flowing out fuel ratio, to flow into fuel many, and since moment t1, the pressure in the 1st control room 51 and the 2nd control room 52 begins to reduce (with reference to " the control room pressure movement " among Fig. 6).
And when the power hour (moment t2 among Fig. 6) that the force rate towards forward end that acts on the valve member 22 boosts valve member 22, valve member 22 beginnings are moved to terminal side.That is, valve member 22 begins to promote (with reference to " the nozzle lifting movement " among Fig. 6).
Moment t3 in Fig. 6, valve member 22 has become the clear way valve state, and this moment, instruction piston 25 made recess 43 butts of its base end part and orifice plate 41, so that seal the opening in the 2nd control room 52 shown in Fig. 4 (b).Thus, as mentioned above, the 1st control room 51 and the 2nd control room 52 become the state (with reference to Fig. 5 (b)) that is communicated with by pressure regulation throttling stream 61.At this moment, because fuel is limited to the 2nd the mobile of control room 52 from the 1st control room 51, therefore between the 1st control room 51 and the 2nd control room 52, produce pressure difference.Specifically, the fuel pressure in the fuel pressure in the 1st control room 51 ratio control room in the past is big, and the fuel pressure in the fuel pressure ratio control room in the past in the 2nd control room 52 is little.
Next, the moment t4 in Fig. 6, when supplying with when finishing to the driving current of coil 36 from ECU140, the valve 37a of control valve 37 by the power that applies of spring 38 once more with orifice plate 41 butts.Thus, in the 2nd control room 52,56 be closed, so its fuel pressure rises owing to portal.And at moment t5, the pressure in the 1st control room 51 and the 2nd control room 52 becomes identical.Wherein, because the fuel pressure in the 1st control room 51 changes under high relatively state by pressure regulation throttling stream 61, therefore at this moment t5, the pressure ratio in the 1st and the 2nd control room 51,52 was big in the past.
In formation in the past, moment t4 the valve 37a of control valve 37 by the power that applies of spring 38 once more with orifice plate 41 butts after, because the pressure in control room can sharply not rise, therefore the moment t7 from Fig. 6, valve member 22 begin the forward end side shiftings, and at the moment t9 spray orifice are closed valve.Relative with it, in the present embodiment,, spray orifice is closed valve therefore since moment t6 (the Zao moment of t7 in the ratio moment), valve member 22 forward end side shiftings, and at moment t8 (than the Zao moment of t9 in the moment) because the fuel pressure of moment t5 is bigger than in the past.Promptly, in the past, from being " valve-closing time " by ECU140 to the time that begins till the moment t9 finish time (t4 constantly) that the driving current of coil 36 is supplied with, with it relatively in the present embodiment, the time till from moment t4 to moment t8 is " valve-closing time ".
As above detailed description the in detail, constitute in the present embodiment, constitute the control room by the 1st control room 51 and the 2nd control room 52, under the state that the fuel pressure in control room becomes low relatively, be communicated with the 1st control room 51 and the 2nd control rooms 52 by pressure regulation throttling stream 61.Thus, because fuel is limited to the 2nd the mobile of control room 52 from the 1st control room 51, therefore between the 1st control room 51 and the 2nd control room 52, produce pressure difference.Here, as the valve 37a of control valve 37 during once more with orifice plate 41 butts, pressure in moment t5, the 1st control room 51 and the 2nd control room 52 becomes identical, but because the fuel pressure in the 1st control room 51 changes under high relatively state by pressure regulation throttling stream 61, therefore the pressure ratio in this moment t5, the 1st and the 2nd control room 51,52 was big in the past.Therefore, can cross shortening portals from sealing and 56 begins to the time (with reference to Fig. 6) of valve member till assigned position (closing valve position) moves.
In addition, above-mentioned pressure regulation throttling stream 61 is by instructing the base end part and orifice plate 41 butts of piston 25 to form.In this sense, become " pressure regulation throttling stream is formed on the abutting part of board of valve member butt ".
The hydraulic pressure of the 2nd mode of execution constitutes as shown in Figure 7.Fig. 7 is the local amplification sectional view of the formation of expression sparger 90.
As shown in Figure 7, the base end part of instruction piston 250 becomes the less relatively minor diameter part 250a of diameter.Thus, around the minor diameter part 250a of instruction piston 250, form the 1st control room 510.And, form the 2nd control room 520 cylindraceous in the part of the central shaft that comprises orifice plate 410.In addition, orifice plate 410 constitutes " board ".
Via the paths 17,19 that form in shell 13 inside with at the orifice plate 410 inner paths 530 that form, to the 1st control room 510 fuelings.Here, be formed with hand-hole 550, by this hand-hole 550 communication paths 530 and the 1st control room 510 in orifice plate 410 inside.Hand-hole 550 plays the effect of supply side throttling.In this sense, hand-hole 550 constitutes " supply side throttling stream ".
On the other hand, when control valve 37 was moved upward, the fuel in the 2nd control room 520 was via portalling 560, spilling at the main body 34 inner fuel chambers 57 that form, the path 58 that is connected with fuel chambers 57, the path 59 that is connected with path 58.On the other hand, when control valve 37 and orifice plate 410 butts, portal 560 by valve 37a sealing, fuel is not discharged from.Portal and 560 play the effect of discharging the side throttling.In this sense, portal and 560 constitute " discharging side throttling stream ".
Here, particularly shown in Fig. 7 (a) like that, moved at instruction piston 250 under the state (promote state) of terminal side, the 1st control room 510 and the 2nd control room 520 are by 610 connections of pressure regulation throttling stream.Shown in Fig. 7 (b), this pressure regulation throttling stream 610 is formed by the stria radially that forms on the cardinal extremity face of instruction piston 250.On the other hand, having moved under the state (the not state of Ti Shenging) of forward end at instruction piston 250, works as 1 control room in the 1st control room 510 and the 2nd control room 520.That is, under the state that instruction piston 250 does not promote, pressure regulation throttling stream 610 is inoperative.In addition, also constitute and identical fuel path shown in Figure 5 in this case.
Also can realize the effect identical by this formation with above-mentioned mode of execution.In addition, above-mentioned pressure regulation throttling stream 610 is formed by the stria of orifice plate 410 with the cardinal extremity face of instruction piston 250.That is, become " pressure regulation throttling stream is formed by the recess of the cardinal extremity face of board and valve member ".
The hydraulic pressure of the 3rd mode of execution constitutes shown in Fig. 8 (a).Fig. 8 (a) is the local amplification sectional view of the formation of expression sparger 91.
Shown in Fig. 8 (a), the base end part of instruction piston 251 becomes the less relatively minor diameter part 251a of diameter.Thus, around the minor diameter part 251a of instruction piston 251, form the 1st control room 511.And, form the 2nd control room 520 cylindraceous in the part of the central shaft that comprises orifice plate 410.In addition, because the structure of orifice plate 410 is with above-mentioned identical, so given identical symbol.And it is also identical that orifice plate 410 constitutes " board " this situation.
Via the paths 17,19 that form in shell 13 inside with at the orifice plate 410 inner paths 530 that form, to the 1st control room 511 fuelings.Here, be formed with hand-hole 550, by this hand-hole 550 communication paths 530 and the 1st control room 511 in orifice plate 410 inside.Hand-hole 550 plays the effect of supply side throttling.In this sense, hand-hole 550 constitutes " supply side throttling stream ".
On the other hand, when control valve 37 when terminal side moves, the fuel in the 2nd control room 520 is via portalling 560, spilling at the valve body 34 inner fuel chambers 57 that form, the path 58 that is connected with fuel chambers 57, the path 59 that is connected with path 58.On the other hand, when control valve 37 and orifice plate 410 butts, portal 560 by valve 37a sealing, fuel is not discharged from.Portal and 560 play the effect of discharging the side throttling.In this sense, portal and 560 constitute " discharging side throttling stream ".
Here, particularly shown in Fig. 8 (a) like that, moved at instruction piston 251 under the state (promote state) of terminal side, the 1st control room 511 and the 2nd control room 520 are by 611 connections of pressure regulation throttling stream.Shown in Fig. 8 (b), this pressure regulation throttling stream 611 forms, on the base end part of instruction piston 251 from the centroclinal through hole of cardinal extremity face.On the other hand, having moved under the state (the not state of Ti Shenging) of forward end at instruction piston 251, works as 1 control room in the 1st control room 511 and the 2nd control room 520.That is, under the state that instruction piston 251 does not promote, pressure regulation throttling stream 611 is inoperative.In addition, also constitute fuel path same as shown in Figure 5 in this case.
Also can realize the effect identical by this structure with above-mentioned mode of execution.In addition, above-mentioned pressure regulation throttling stream 611 forms the through hole on the base end part of instruction piston 251.That is, form " pressure regulation throttling stream for the base end part of the valve member of board butt on through hole ".
The hydraulic pressure of the 4th mode of execution constitutes as shown in Figure 9.Fig. 9 is the local amplification sectional view of the formation of expression sparger 92.
As shown in Figure 9, the base end part of instruction piston 252 is the less relatively minor diameter part 252a of diameter.Thus, around the minor diameter part 252a of instruction piston 252, form the 1st control room 512.And, form the 2nd control room 522 cylindraceous in the part of the central shaft that comprises orifice plate 412.In addition, orifice plate 412 constitutes " board ".
Via the paths 17,19 that form in shell 13 inside with at the orifice plate 412 inner paths 532 that form, to the 1st control room 512 fuelings.Here, be formed with hand-hole 552, by this hand-hole 552 communication paths 532 and the 1st control room 512 in orifice plate 412 inside.Hand-hole 552 plays the effect of supply side throttling.In this sense, hand-hole 552 constitutes " supply side throttling stream ".And, be formed with pressure regulation throttling stream 612 in orifice plate 412 inside, by this pressure regulation throttling stream 612 communication paths 532 and the 2nd control room 522.Pressure regulation throttling stream 612 constitutes " pressure regulation throttling stream ".
On the other hand, when control valve 37 when terminal side moves, the fuel in the 2nd control room 522 is via portalling 562, spilling at the valve body 34 inner fuel chambers 57 that form, the path 58 that is connected with fuel chambers 57, the path 59 that is connected with path 58.On the other hand, when control valve 37 and orifice plate 412 butts, portal 562 by valve 37a sealing, fuel is not discharged from.Portal and 562 play the effect of discharging the side throttling.In this sense, portal and 562 constitute " discharging side throttling stream ".
Here, moved under the state (not promoting state) of forward end at instruction piston 252, because the 2nd control room 522 is to the 1st control room 512 openings, therefore work as 1 control room in the 1st control room 512 and the 2nd control room 522.Figure 10 (a) schematically expresses this form.That is, shown in Figure 10 (a), construct following path (path shown in arrow C and the D): path 532 → hand-hole 552 and pressure regulation throttling stream 612 → control room 512, the 522 → 562 → fuel chambers 57 of portalling.
On the other hand, moved under the state (state of lifting) of terminal side at instruction piston 25, the base end part of instruction piston 252 and orifice plate 412 butts are so that seal the opening in the 2nd control room 522.At this moment, the 1st control room 512 and the 2nd control room 522 are separated, from pressure regulation throttling stream 612 to the 2nd control room fueling.Figure 10 (b) schematically expresses this form.That is, shown in Figure 10 (b), construct following path: path 532 → hand-hole 552 → the 1st control room 512 (path shown in the arrow F); And, path 532 → pressure regulation throttling stream 612 → the 2nd control rooms 522 → 562 → fuel chambers 57 of portalling (path shown in the arrow E).
Also can realize the effect identical by this formation with above-mentioned mode of execution.In addition, above-mentioned pressure regulation throttling stream 611 becomes the intercommunicating pore of orifice plate 412 inside of instruction piston 252 butts.That is, form " pressure regulation throttling stream be the fuel passage of inside of board of valve member butt and the intercommunicating pore in the 2nd control room ".
The present invention is not limited to above-mentioned mode of execution, can implement in every way in the scope that does not exceed invention spirit.
Claims (2)
1. fuel injection system is characterized in that having:
Valve member is supported to can be to moving axially;
Outer cover formation portion supports above-mentioned valve member, and forms the 1st control room at the terminal side of above-mentioned valve member, and the 1st control room makes above-mentioned valve member to moving axially by the fuel pressure of inside;
Board forms to the 2nd control room of above-mentioned the 1st control room opening, and when the fuel pressure in the above-mentioned the 1st and the 2nd control room descended, above-mentioned valve member and this board butt were so that seal above-mentioned opening;
Supply side throttling stream is used for the fuel from inlet side is supplied to above-mentioned the 1st control room via throttling;
Pressure regulation throttling stream is used for the fuel from inlet side is supplied to above-mentioned the 2nd control room via throttling, and the fuel pressure in above-mentioned the 1st control room is maintained fuel pressure height than above-mentioned the 2nd control room; And
Discharge side throttling stream, be used for fuel is discharged to outlet side via throttling from above-mentioned the 2nd control room,
Under the state of above-mentioned valve member and above-mentioned board butt, flow to the fuel in above-mentioned the 2nd control room from above-mentioned the 1st control room and to be blocked, and only by above-mentioned pressure regulation throttling stream to the fuel of above-mentioned the 2nd control room supply from inlet side.
2. fuel injection system as claimed in claim 1 is characterized in that,
Above-mentioned pressure regulation throttling stream forms the fuel passage of board inside of above-mentioned valve member butt and the intercommunicating pore in above-mentioned the 2nd control room.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP236831/2008 | 2008-09-16 | ||
| JP2008236831A JP4716142B2 (en) | 2008-09-16 | 2008-09-16 | Fuel injection device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101676548A CN101676548A (en) | 2010-03-24 |
| CN101676548B true CN101676548B (en) | 2011-12-21 |
Family
ID=42029227
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009101707396A Expired - Fee Related CN101676548B (en) | 2008-09-16 | 2009-09-09 | Fuel injection apparatus |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4716142B2 (en) |
| CN (1) | CN101676548B (en) |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1380939A (en) * | 2000-05-23 | 2002-11-20 | 罗伯特·博施有限公司 | Fuel injection valve |
| CN1636109A (en) * | 2002-02-22 | 2005-07-06 | Crt公共铁路技术公司 | Fuel jetting valve used for internal combustion engine |
| CN1969121A (en) * | 2004-06-03 | 2007-05-23 | 博世株式会社 | Fuel injection valve |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3729534B2 (en) * | 1995-05-25 | 2005-12-21 | 株式会社日本自動車部品総合研究所 | Accumulated fuel injection system |
| JP2005344630A (en) * | 2004-06-03 | 2005-12-15 | Denso Corp | Fuel injection valve of internal combustion engine |
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2008
- 2008-09-16 JP JP2008236831A patent/JP4716142B2/en not_active Expired - Fee Related
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2009
- 2009-09-09 CN CN2009101707396A patent/CN101676548B/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1380939A (en) * | 2000-05-23 | 2002-11-20 | 罗伯特·博施有限公司 | Fuel injection valve |
| CN1636109A (en) * | 2002-02-22 | 2005-07-06 | Crt公共铁路技术公司 | Fuel jetting valve used for internal combustion engine |
| CN1969121A (en) * | 2004-06-03 | 2007-05-23 | 博世株式会社 | Fuel injection valve |
Non-Patent Citations (2)
| Title |
|---|
| JP特开2005-344630A 2005.12.15 |
| JP特开8-319917A 1996.12.03 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101676548A (en) | 2010-03-24 |
| JP4716142B2 (en) | 2011-07-06 |
| JP2010071113A (en) | 2010-04-02 |
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