CN100368679C - Injector having structure for controlling nozzle needle - Google Patents
Injector having structure for controlling nozzle needle Download PDFInfo
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- CN100368679C CN100368679C CNB2005100668682A CN200510066868A CN100368679C CN 100368679 C CN100368679 C CN 100368679C CN B2005100668682 A CNB2005100668682 A CN B2005100668682A CN 200510066868 A CN200510066868 A CN 200510066868A CN 100368679 C CN100368679 C CN 100368679C
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Abstract
A valve back pressure chamber is provided to exert a back pressure of a first valve needle. Furthermore, a hydraulic pressure passage is provided to extend through the valve back pressure chamber. A valve body is provided to a second valve needle and is driven to connect and disconnect between the hydraulic pressure passage and a fuel tank and thereby to drive the first valve needle. The second valve needle is driven by hydraulic pressure induced by an actuator.
Description
Technical field
The present invention relates to sparger, relate in particular to the structure of the nozzle needle that is used to control sparger, this sparger can be driven the injection that is used to allow and forbid fuel.
Background technique
In the sparger that in the common rail type fuel injection system of diesel engine, uses, be driven be used to allow with the nozzle needle of prohibition of fuel injection by actuator for example solenoid control, thereby fuel injection time and fuel injection amount freely are set and realize that thus senior fuel sprays.A kind of sparger of Ti Chuing comprises the nozzle needle back pressure chamber before this, and this nozzle needle back pressure chamber is applying back pressure (for example, announcing referring to the Japanese uncensored patent that is numbered H08-49620) to nozzle needle immediately when supplying with pressurized fuel.When the pressure of nozzle needle back pressure chamber increased or reduces, nozzle needle moved between with respect to the seated position of valve seat and raised position.Release channel and control valve chamber form in sparger.Release channel discharges the pressure of nozzle needle back pressure chamber to low pressure source, and controls the intermediate portion that valve chamber forms release channel.Be driven and be used to allow or when interrupting connection between nozzle needle back pressure chamber and the low pressure source, the pressure of nozzle needle back pressure chamber increases or reduces when being arranged in the control valve of control in the valve chamber.Control valve can be sat the valve seat that forms in the excircle part of the port of controlling valve chamber, this control valve chamber is communicated with the nozzle needle back pressure chamber.The fuel pressure of port is applied on the control valve along the direction of opening of valves, and spring force is applied on the control valve along the valve closing direction.When solenoid attraction formed the armature of an integral body with control valve, the control valve against was lifted.
At this, the closed state of retentive control valve when spring force is arranged in the solenoid outage.Determine the gravitation that solenoid is required based on spring force.
In the time of need realizing size when actuator and reduce (for example solenoidal size reduces), owing to long-pending the reducing of solenoidal magnetic surface causes solenoidal attraction force also to descend.Therefore, spring force also should reduce and the fuel pressure that is applied on the control valve along direction of improvement also should reduce.
The pressure receiving surface is long-pending to be reduced so that reduce to be applied to the diameter that fuel pressure on the control valve can be by reducing the control valve valve seat fully along direction of improvement.Yet owing to blocking action that reduces to produce or the throttling action by valve-seat diameter, the pressure of nozzle needle back pressure chamber reduces the responsiveness that speed can too slowly influence nozzle needle.In addition, when the hole is provided at the pressure that is used to adjust the nozzle needle back pressure chamber in the release channel and reduces speed, owing to above-mentioned throttling action makes adjustable scope relative narrower.When the opening state lower channel cross sectional area at control valve need increase, the amount of lifting of control valve can increase.Yet the distance between the attraction force of solenoid valve and armature and the magnetic pole is inversely proportional to.Therefore, under the situation of the amount of lifting that increases control valve, need relatively large gravitation and therefore can not realize reducing of solenoid size.
Summary of the invention
The invention solves above-mentioned shortcoming.Therefore, an object of the present invention is to provide a kind of sparger, this sparger comprises the actuator with minimum dimension and can reach enough passage cross sectional areas when opening controlling valve.
In order to realize one object of the present invention, provide a kind of sparger that comprises slender substrate.Thereby spray-hole penetrates the wall of matrix carries out burner oil.The nozzle box directly with matrix in the upstream side of spray-hole on spray-hole be communicated with and supply with pressurized fuel.Nozzle needle is arranged in the nozzle box and is driven and is used to allow or forbids spraying via the fuel of spray-hole.The pedestal end place of the nozzle needle of nozzle needle back pressure chamber in premature forms, thereby and supplies with pressurized fuel and be used for applying back pressure so that towards spray-hole pushing nozzle needle to nozzle needle.Release channel is formed for discharging to outside low pressure source the pressure of nozzle needle back pressure chamber in matrix.The control valve chamber is arranged in the intermediate portion of the release channel of matrix.First control valve is arranged in the control valve chamber and is driven and is used for connecting or disconnecting nozzle needle back pressure chamber and low pressure source.The valve drive that is used to drive first control valve is provided.Valve drive is the hydrovalve drive unit that comprises hydraulic channel, second control valve and actuator.Hydraulic channel forms in matrix, and like this, hydraulic channel is supplied to pressurized fuel and provides pressurized fuel as the control hydraulic fluid that is used to drive first control valve to first control valve.Second control valve is driven the fuel flow rate that is used for controlling hydraulic channel.Actuator drives second control valve.
Description of drawings
After explanation, appended claims and the accompanying drawing below having read, will understand the present invention and attached purpose therewith, feature and advantage best, among the figure:
Fig. 1 is the sectional view according to the sparger of first embodiment of the invention;
Fig. 2 is the local amplification view of first embodiment's sparger;
Fig. 3 is the Schedule of various serviceability that has shown first embodiment's sparger;
Fig. 4 A is the sectional view of first embodiment's sparger, has shown the closed state of nozzle needle;
Fig. 4 B is the sectional view of first embodiment's sparger, has shown the opening state of nozzle needle;
Fig. 5 has shown the schematic representation as the fuel stream of control fluid according to first embodiment;
Fig. 6 has shown according to the schematic representation of the technology that proposes before this as the fuel stream of control fluid;
Fig. 7 is the figure of operation that has shown first embodiment's sparger;
Fig. 8 is the local amplification view of sparger according to a second embodiment of the present invention;
Fig. 9 is the time diagram that has shown first embodiment's operating characteristics, has shown the technical background of the third embodiment of the present invention;
Figure 10 is the schematic representation of a part that has shown first embodiment's sparger, has shown the 3rd embodiment's technical background;
Figure 11 is the sectional view according to the sparger of third embodiment of the invention;
Figure 12 is the schematic sectional view of manufacture process that has shown the 3rd embodiment's sparger;
Figure 13 is the time diagram that has shown the 4th embodiment's technical background;
Figure 14 is the local amplification view of the sparger of a fourth embodiment in accordance with the invention;
Figure 15 is the result who has shown operation simulation, has shown the advantage of continuous connecting passage among the 4th embodiment;
Figure 16 is the local amplification view of first embodiment's sparger, and it does not have continuous connecting passage such among the 4th embodiment;
Figure 17 has shown the figure that the sparger of Figure 16 is carried out the result of operation simulation;
Figure 18 is the local amplification view of sparger according to a fifth embodiment of the invention;
Figure 19 is the local amplification view of sparger according to a sixth embodiment of the invention;
Figure 20 is the local amplification view that is used for example sparger relatively;
Figure 21 is the local amplification view of sparger according to a seventh embodiment of the invention;
Figure 22 A is the enlarged view of the part XXIIA that shown that Figure 21 centre circle gets up, has shown the closed state of sparger safety check;
Figure 22 B is and view like Figure 22 category-B to have shown the opening state of the safety check of sparger;
Figure 23 A is the local amplification view according to the sparger of the eighth embodiment of the present invention;
The sectional view of the line XXIIIB-XXIIIB of Figure 23 B in Figure 23 A;
The sectional view of the line XXIIIC-XXIIIC of Figure 23 C in Figure 23 A;
Figure 24 is the local amplification view of the 8th embodiment's sparger, has shown a kind of serviceability of first needle of sparger; And
Figure 25 is and the similar view of Figure 24 to have shown the another kind of serviceability of first needle of sparger.
Embodiment
(first embodiment)
Fig. 1 and 2 has shown the structure according to the sparger of first embodiment of the invention.Sparger is used in the internal-combustion engine, for example is used in the diesel engine with common rail type fuel injection system and sets on each cylinder of motor.Sparger is used in the predetermined time cycle fuel from rail supply altogether being sprayed by ECU control.
Sparger comprises the slender substrate 2 that is generally cylindrical configuration.Matrix 2 comprises nozzle body 21, partition 22, first valve body 23, support 24 and set screw nut 25.Nozzle body 21, partition 22, valve body 23 and support 24 are distolateral from the downstream of sparger to be arranged vertically and is clamped together by set screw nut 25 with this order.
Each recess and hole are formed on and are used to hold corresponding part in the matrix 2 and form fuel channel.Put in nozzle arrangements 11 in the firing chamber of corresponding cylinder and be provided in the lower end of sparger, this lower end is the bottom in Fig. 1.Nozzle arrangements 11 comprises nozzle body 21.Vertically extend along the axial direction of matrix 2 in hole 211, and nozzle needle 31 is contained in vertical hole 211.Tubular member 21a advances in vertical hole 211 in nozzle body 21 upper end press fit, and the upper end of nozzle needle 31 is slidingly received among the tubular member 21a.Vertically the lower end in hole 211 extends to the following far-end of nozzle body 21 and forms nozzle box 51.Spray-hole 52 penetrates the base wall of the nozzle box 51 of nozzle body 21.On the lower end side of the slide part of nozzle needle 31, vertically hole 211 be communicated with as fuel supply channel and high-pressure channel 61 formation in partition 22, first valve body 23 and support 24.When nozzle needle 31 promotes away from the valve seat that is provided in 51 places, nozzle box, spray through spray-hole 52 from the pressurized fuel (fuel under high pressure) that is total to the rail supply.
Thereby helical spring 32 is contained in vertical hole 211 and is clamped in the direction pushing nozzle needle 31 of promptly sitting down in a downward direction around the nozzle needle 31.The nozzle needle back pressure chamber 53 that applies back pressure to nozzle needle 31 is above the position of the pedestal end of adjacent nozzles nozzle needle 31 is defined in the slide part of nozzle needle 31.More particularly, partition 22 forms the upper wall of nozzle needle back pressure chamber 53, and the upper end of nozzle needle 31 (pedestal end) forms the lower wall of nozzle needle back pressure chamber 53.31 direction of improvement promptly is applied on the nozzle needle 31 away from the direction of valve seat fuel pressure from high-pressure channel 61 along nozzle needle.When the pressure of nozzle needle back pressure chamber 53 becomes when being equal to or less than predetermined opening of valves starting pressure, nozzle needle lifts from valve seat.When the pressure of nozzle needle back pressure chamber 53 becomes when being equal to or greater than predetermined valve and closing kinetic pressure, thereby nozzle needle is sitting in and stops fuel on the valve seat and spray.
Carry out the pressure conversion of nozzle needle back pressure chamber 53 by following structure.Vertically hole 231 axial direction along sparger in first valve body 23 extends, thereby and vertically the cross sectional area of 231 lower ends, hole enlarge the hole enlargement part (part that cross sectional area enlarges) that forms vertical hole 231, this part constitutes first control valve chamber 54.First needle 33 that serves as first control valve is arranged in the first control valve chamber 54.First needle 33 has the neck that diameter reduces near forming cylindrical body and being included in the lower end.In Fig. 2, be positioned at the minor diameter part slidably clamping of the axial region 33b of first needle 33 above first needle, 33 necks by vertical hole 231.The lower end side that is arranged in first needle 33 of first needle, 33 necks below puts in the first control valve chamber 54 and forms valve body 33a.The diameter of the first needle valve body 33a is slightly greater than the diameter of axial region 33b, and forms annulus between the inner peripheral wall surface of the first needle valve body 33a and the first control valve chamber 54.Thereby the top and bottom of first needle valve body 33a chamfering respectively have the conical surface.First needle 33 is pushed downwards by the spring force of helical spring 34.
High pressure affluent channel (communication passage) 64 with hole (restriction) forms in first valve body 23 with first control valve chamber 54.High pressure affluent channel 64 is communicated with from high-pressure channel 61 shuntings and with the first control valve chamber 54.In the far-end of the neck place of first needle 33 high pressure affluent channel 64 peripheral wall surface, open and be communicated with the excircle annulus 333 of the neck of first needle 33 all the time in vertical hole 231.Low pressure affluent channel 65 forms in partition 22.Low pressure affluent channel 65 is communicated with from low-pressure channel 62 shuntings and with the first control valve chamber 54.Low pressure affluent channel 65 the relative position relative with the rear surface of the first needle valve body 33a be in first control valve chamber 54 wall surfaces in open.The opening end of low pressure affluent channel 65 forms port 65a.When first needle 33 move down and with the wall surfaces of the first control valve chamber 54 port 65a closure when engaging.The outer periphery of this opening end of low pressure affluent channel 65 forms the valve seat (valve seat of below) that first needle 33 is sat.When first needle 33 moved up, the last tapering of the first needle valve body 33a was sitting on the ladder surface of the first control valve chamber 54, and this ladder surface forms valve seat (upper valve base) 542.
The hole 651 of serving as restriction is in formation in the low pressure affluent channel 65 at the downstream position that is close to of port 65a.
The valve driving device 12 of hereinafter description being served as the valve drive (fluid pressure drive device) that is used to control first needle 33.Via the increase of valve back pressure chamber 55 pressure that form above axial region 33b or reduce, first needle 33 moves.Valve back pressure chamber 55 receives fuel under high pressure next from high-pressure channel 61 and high pressure affluent channel 64 via the sidewise hole 332 of the vertical hole 331 and first needle 33.Vertically the neck that arrives first needle 33 is extended from the upper end face of first needle 33 in hole 331.Sidewise hole 332 arrives vertical hole 331 from the neck that the external peripheral surface of first needle 33 radially extends in first needle 33.
Valve back pressure chamber 55 is communicated with via communication passage 66 with the second control valve chamber 56.Communication passage 66 forms the path hole of extending the upper end face that arrives first valve body 23 from 231 tops, vertical hole of first valve body 23.Hole (restriction) 661 forms in the neutral position of communication passage 66.
The second control valve chamber 56 forms by first valve body 23 and the groove that forms in second valve body, 26 rear surfaces.First valve body 23 forms the lower end wall of the second control valve chamber 56.The outer periphery 26a of the rear surface groove of second valve body 26 forms the projection of ring-type, and this projection press fit is to the circular groove that forms in first valve body, 23 upper end faces, and like this, first valve body 23 and second valve body 26 just are assembled together.
In the second control valve chamber 56, the opening end of the communication passage 66 of opening at the wall surfaces place of the second control valve chamber 56 forms the port 66a that is communicated with valve back pressure chamber 55.The second control valve chamber 56 is communicated with low-pressure channel 62 all the time in its outer circumference.
The lower end clamping of second needle 36 is used to serve as the valve body 35 of second control valve with semi-spherical shape.Second needle 36 integrally moves with valve body 35.It is relative with port 66a that valve body 35 flat rear surfaces and second are controlled the wall surfaces of valve chamber 56.The seat surface 561 that valve body 35 is sat forms in the outer periphery of port 66a.When valve body 35 is sat to seat surface 561, just disconnected the connection between second valve chamber 56 and the valve back pressure chamber 55.
Circular dish type armature 37 is fixed to the upper end that puts in second needle 36 in the solenoid chamber 57.Armature 37 is relative with the pole surface of solenoid (actuator) 121 in being arranged in solenoid chamber 57.In solenoid 121, coil 42 twines round the annulus of stator 41, and this space comprises two coaxial cylindrical bodys.Electric energy is supplied with coil 42 from lead 43.Helical spring 38 radially inwardly be contained in the stator 41 and with armature 37 Elastic Contact.Helical spring 38 is along the direction pushing armature 37 away from stator 41.Solenoid 121 is sandwiched between second valve body 26 and the enclosed member 27 and with second valve body 26 and enclosed member 27 and is contained in vertical hole 241 of support.Sealing component 44 is sealed between enclosed member 27 and the support 24.
Fig. 3 is the time diagram that is used to describe the operation of sparger.When solenoid 121 was opened, nozzle needle 31 lifted away from valve seat, and the result is the opening of valves of nozzle needle 31.When solenoid 121 was closed, nozzle needle 31 was sat to valve seat, and the result is the valve closure of nozzle needle 31.Fig. 4 A has shown the state the when valve of nozzle needle 31 is closed, the state when Fig. 4 B has shown the opening of valves of nozzle needle 31.When solenoid 121 energisings, solenoid 121 attracts armature 37, and second needle 36 moves up as a result.At this, the sidewise hole 332 of high-pressure channel 61, high pressure affluent channel 64, first needle 33, vertical hole 331 of first needle 33, valve back pressure chamber 55, communication passage 66, the second control valve chamber 56 and low-pressure channel 62 form hydraulic channel.In this hydraulic channel, the fuel in the valve back pressure chamber 55 turns back to the fuel tank 3 (Fig. 5) that serves as low pressure source via communication passage 66, the second control valve chamber 56 and low-pressure channel 62 successively.First needle 33 lifts and sits to upper valve base 542 away from lower valve base 541.In this state, because first needle 33 is sitting on the upper valve base 542, thus just disconnected first connection of controlling between valve chamber 54 and the high-pressure channel 61, and interrupted supplying with fuel under high pressure to the first control valve chamber 54.In addition, because first needle 33 lifts away from lower valve base 541, just opened the release channel that comprises communication passage 63, first control valve chamber 54, low pressure affluent channel 65 and low-pressure channel 62.Therefore, the fuel of nozzle needle back pressure chamber 53 turns back to fuel tank 3, like this pressure of nozzle needle back pressure chamber 53 be discharged to fuel tank 3 and thus pressure reduce.When the pressure of nozzle needle back pressure chamber 53 becomes when being equal to or less than predetermined opening of valves starting pressure, nozzle needle 31 lifts promptly and opens.
On the contrary, when solenoid 121 is closed when being no electric circuit, and when therefore second needle 36 moved down, the connection between valve back pressure chamber 55 and the low-pressure channel 62 had just disconnected.Therefore, increase owing to fuel under high pressure makes the pressure of valve back pressure chamber 55, wherein this fuel under high pressure via comprise high-pressure channel 61, high pressure affluent channel 64, first needle is 33 sidewise holes 332 and the passage supply valve back pressure chamber 55 in vertical hole 331 first needle 33.Like this, first needle 33 lifts away from upper valve base 542 and sits to lower valve base 541.In this state, the connection between the first control valve chamber 54 and the low pressure chamber 62 disconnects, and fuel under high pressure is supplied with nozzle needle back pressure chamber 53 via the respective channel that comprises high-pressure channel 61, high pressure affluent channel 64, the first control valve chamber 54 and communication passage 63.So increased the pressure of nozzle needle back pressure chamber 53.When the pressure of nozzle needle back pressure chamber 53 becomes when being equal to or greater than predetermined valve and closing kinetic pressure, nozzle needle 31 is sat and is promptly placed the valve closed state to valve seat.
The sparger of present embodiment constitutes in above-mentioned mode.Fig. 5 has shown the schematic representation according to the control system of first embodiment's nozzle needle 31.Formerly in the sparger as shown in Figure 6 of Ti Chuing, the use of three-way valve 33a is with shown in Figure 5 identical, and wherein three-way valve 33a is as the needle of controlling nozzle needle 31 by the back pressure of conversion nozzle needle 31 between high pressure and low pressure.Yet with regard to Fig. 6, needle 33a is directly driven by solenoid 121a.On the contrary, with regard to sparger as shown in Figure 5, needle 33 is by hydraulic control, and in turn this hydraulic pressure is by solenoid 121 controls.Therefore, be different from before this sparger as shown in Figure 6 that proposes, it can be not be provided with required driving force according to the specification of solenoid 121,121a.
Like this, the amount of lifting of the valve-seat diameter and first needle 33 can be made fully big, no matter and the size of solenoid 121 how.Therefore, the operating characteristics of nozzle needle 31 can more freely be adjusted by being provided in the hole 631 that has been communicated with the nozzle needle back pressure chamber 53 and the first control valve chamber 54 in the communication passage 63.
Fig. 7 shown valve by the situation of solenoid-activated under valve the amount of lifting and realize this amount of lifting of valve relation between the required time (valve opening time).More particularly, when the path solenoid to magnetic pull with less attraction armature compared with the big footpath solenoid with the big magnetic pull that attracts armature, big footpath solenoid was because its bigger magnetic pull has shown the valve opening time of weak point.Yet, under the less situation of the amount of lifting of valve, do not have marked difference between path solenoid and the big footpath solenoid.Therefore, even using under the solenoidal situation of the inadequate path of the driving force that is directly used in actuating valve that is had, just as sparger of the present invention, when control valve by hydraulic driving and when being used to open control valve with closed hydraulic channel and driving by the path solenoid, valve opening time can not worsen substantially yet.Perhaps, can shift to an earlier date the measuring operation response characteristic, and can respond fuel injection time and solenoidal cycle current"on"time is proofreaied and correct, wherein need this fuel injection time to come error in the compensating operation response based on the measurement result of operation response characteristic.
In addition, in the sparger of present embodiment, as mentioned above, the contiguous place of the port 65a of hole 651 on the downstream side of the port 65a of low pressure affluent channel 65 forms, and this low pressure affluent channel 65 reaches low-pressure channel 62 from the port 65a of the first control valve chamber 54.Therefore, though when first needle 33 when lower valve base 541 lifts because the throttling action in hole 651, the pressure in the space between first needle 33 and the lower valve base 541 can promptly not reduce.Therefore, when lifting, lower valve base 541 kept higher relatively pressure in the space between first needle 33 and the lower valve base 541 when first needle 33.The acceleration direction that this residual pressure quickens along the opening of valves to first needle 33 by the lifting of auxiliary first needle 33 applies, and this residual pressure also applies along the direction that is used to make first needle 33 keep promoting.Therefore, improve the operational stability of first needle 33, and can reduce the operation variation of sparger.
(second embodiment)
Fig. 8 has shown sparger according to a second embodiment of the present invention.In this embodiment, change has taken place in the part of the structure of first embodiment's sparger, and with the similar parts of first embodiment by identical numeral.In the following description, will parts different with first embodiment in the emitter construction be described mainly.
Second embodiment's matrix 2A is basically the same as those in the first embodiment basically.Yet second embodiment's partition 22A is different with enclosed member 27 with first embodiment's partition 22 with enclosed member 27A.Thereby form among partition 22A from high-pressure channel 61 shunting and the high pressure affluent channel 67 that is communicated with nozzle needle back pressure chamber 53 and to be communicated with nozzle needle back pressure chamber 53 and high-pressure channel 61 all the time.Hole (restriction) 671 forms in high pressure affluent channel 67.Like this, as shown in Figure 3, when the opening of valves of nozzle needle 31, even when first needle 33 lifts and sit to upper valve base 542 from lower valve base 541, the fuel under high pressure of prearranging quatity is via high pressure affluent channel 67 supply nozzle nozzle needle back pressure chambers 53.Therefore, carry out the opening of valves of nozzle needle 31 with the speed of appropriateness.On the contrary, when first needle 33 lifts and sits to lower valve base 541 from upper valve base 542, with comparing of first embodiment, because the inflow of the fuel in the high pressure affluent channel 67, so the pressure of nozzle needle back pressure chamber 53 promptly increases.Therefore, nozzle needle 31 is promptly sat down.Because the appropriateness of the valve of nozzle needle 31 is opened, so the amount of the NOx in the waste gas reduces.And, because the quick-make of the valve of nozzle needle 31, so the amount of soot in the waste gas reduces.Can adjust the opening of valves speed and the valve closing speed of nozzle needle 31 by the passage cross sectional area in the hole 671 of communication passage 67.
The structure of armature 37A is basically the same as those in the first embodiment basically.Spacer 39 is provided in the facing surfaces of the armature 37A relative with stator 41.Spacer 39 is circular dish member, has the diameter greater than helical spring 38.Annular projection 39a forms in the outer periphery of spacer 39.Under the upper surface of annular projection 39a and state that stator 41 engages, second needle 36 places the state that lifts fully.Highly be adjusted at state lower armature 37A that second needle 36 lifts fully and the space between the stator 41 by changing being provided with of protruding 39a.
Eliminated the sealing component of enclosed member 27 first embodiment from second embodiment's enclosed member 27A.In a second embodiment, enclosed member 27A press fit is used for so just having reduced the number of parts in enclosed member 27A and vertically sealing between the hole 241 to vertical hole 241.
(the 3rd embodiment)
Fig. 9 is the figure of the pressure of the amount of lifting of nozzle needle 31 and nozzle box 51 in expression first embodiment's the sparger about the fuel injection time cycle.After fuel injection start, the pressure of nozzle box 51 reduces (step-down).It is effectively setting the decline that limits this pressure in the accumulation chamber in high-pressure channel.For example, as shown in figure 10, in first embodiment's sparger, the internal diameter that forms vertical hole 242 of high-pressure channel 61 can be provided so from opposing end faces and enlarges the predetermined degree of depth, and this opposing end faces is relative with first valve body 23 of support 24.Use this structure, the wall of support 24 is substantially in the vertically outer circumference portion office attenuation in hole 241, thereby provides the space for second needle 36 and solenoid 121.In addition, as a possible embodiment, support can be divided into subassembly along the axial direction of sparger so that form the accumulation chamber, and subassembly can be connected to each other mechanically via set screw nut.Yet under this this situation, the become external diameter of more complicated and sparger of structure can increase unfriendly.Present embodiment has solved above-mentioned shortcoming and has improved the practical application of sparger.
Figure 11 has shown the sparger of a third embodiment in accordance with the invention.In this embodiment, change has taken place in the part of the structure of first embodiment's sparger, and with the similar parts of first embodiment by identical numeral.In the following description, will parts different with first embodiment in the emitter construction be described mainly.
The high-pressure channel 61B that forms in the matrix 2B high-pressure channel 61 with first embodiment basically is identical.The difference that only has that exists with first embodiment is that accumulation chamber 58 is provided among the high-pressure channel 61B.Accumulation chamber 58 is arranged in the side in vertical hole 241 at the minor diameter part place that has set the lead 43 that is used to receive vertical hole 241.Like this, can make the outer circle wall of accumulation chamber 58 keep enough thickness.Accumulation chamber 58 forms by following mode.In the present embodiment, as shown in figure 12, when forming support 24B, set two members (distal portion and base ends) 7a, 7b.When the imaginary line that transversely passes through accumulation chamber 58 was divided into two parts with the support 24B of sparger in the axial direction, member 7a, 7b just formed corresponding shape.Each member 7a, 7b have hole 71a, the 71b of a part that forms high-pressure channel 61B and form hole 72a, the 72b of the part in vertical hole 241 when receiving second valve body 26.In the upper component 7b that forms support 24B, the hole 71b that forms high-pressure channel 61B has the wide diameter portion (part that the transverse section enlarges) and the jointing end face (joint end face or joint surface) of formation and member 7b that comprise internal diameter expansion (cross sectional area expansion) and has the predetermined degree of depth, and this member 7b engages with another member 7a.The jointing end face of member 7a, 7b be the cleaning and be engaged with each other.Then, the jointing end face with member 7a, 7b is heated to high temperature.The atom of member 7a, 7b spreads in corresponding scope, and wherein this scope is placed in the middle in the opposing end faces of member 7a, 7b, and therefore, member 7a, 7b link together by diffusion bonding.The wide diameter portion 711 of hole 71b forms accumulation chamber 58.
Like this, the wall at the outer circumference portion office matrix 2B that accumulates chamber 58 just can form accumulation chamber 58 without attenuation.In addition, member 7a, 7b do not connect in the present embodiment mechanically, and like this, the size of sparger can not increase substantially.
(the 4th embodiment)
With reference to Figure 13 the influence of the pressure of the first control valve chamber 54 to the lifting of first needle 33 described below.Described with reference to Figure 3, when the pressure of the valve back pressure chamber 55 that is positioned at first needle, 33 upsides reduced, first needle 33 lifted and sits to upper valve base 542 from lower valve base 541.At this moment, as shown in figure 13, thereby the first control valve chamber 54 produces vibration along unstable first needle 33 that causes of the direction of improvement applied pressure of first needle 33.For example, in first embodiment's sparger, because the existence in hole 651, the pressure of the first control valve chamber 54 keeps higher relatively value, wherein this hole 651 be arranged in the port 65a that will open under.Yet when the power that is produced by valve back pressure chamber 55 (and the spring force that also has helical spring 34 in addition) becomes than by the power that pressure produced of the first control valve chamber 54 when big, first needle 33 lifts from upper valve base 542.Because upper valve base 542 has bigger unlatching zone, so fuel under high pressure flows out from high-pressure channel 61, high pressure affluent channel 64 and the first control valve chamber 54.Therefore, the pressure of the first control valve chamber 54 increases.Since the increase of pressure, the closed upper valve base 542 thereby first needle 33 moves up once more.
When repeating this phenomenon, can cause first needle 33 to produce vibration, and this vibration can cause the variation of fuel injection amount or the wearing and tearing of valve seat conversely.Present embodiment has solved above-mentioned shortcoming and has improved the practical application of sparger.
Figure 14 has shown the sparger according to the embodiment of the invention.In this embodiment, change has taken place in the part of the structure of first embodiment's sparger, and with the similar parts of first embodiment by identical numeral.In the following description, will parts different with first embodiment in the emitter construction be described mainly.
This embodiment's matrix 2C is basically the same as those in the first embodiment basically.Yet the first valve body 23C of formation matrix 2C is different with first embodiment's.In the first valve body 23C, the high pressure affluent channel 64 point punishment stream below from high-pressure channel 61 extends promptly flows in the some punishment of high pressure affluent channel 64 on the upstream side of the opening of the excircle annulus 333 that is positioned at first needle, 33 necks.Thereby this tributary part of high pressure affluent channel 64 is opened in the inner peripheral wall of the first control valve chamber 54 and is formed continuous connecting passage 68, and this passage 68 is communicated with the high-pressure channel 64 and the first control valve chamber 54 all the time.Connecting passage 68 forms the communication passage that directly is communicated with the high pressure affluent channel 64 and the first control valve chamber 54 without excircle annulus 333 continuously.In addition, hole (restriction) 681 is provided in the continuous connecting passage 68.Like this, even when first needle 33 is sat to upper valve base 542, because the restriction in hole 681, a spot of fuel under high pressure is still supplied with the first control valve chamber 54.Therefore, the pressure of the first control valve chamber 54 can excessively not reduce, and therefore can limit the fluctuation of first needle, 33 valve seat positions.
Figure 15 has shown the advantage of the continuous connecting passage 68 of present embodiment, and this operation simulation by sparger has obtained confirmation.Respective point A-F place in Figure 14 measures the represented waveform by the A-F among Figure 15.For relatively, Figure 17 has shown another kind of Simulation result, does not wherein promptly set on the structure of continuous connecting passage 68 and carried out this simulation under equal state in the structure (first embodiment's structure) of Figure 16.In each figure of Figure 15 and 17, the pressure of each appropriate section of sparger is by first expression of the y coordinate that is positioned at the figure left side.And in each figure of Figure 15 and 17, the amount of lifting of each corresponding part of sparger is by second expression of the y coordinate that is positioned at the figure right side.In each figure of Figure 15 and 17, line E represents the pressure of the first control valve chamber 54, and this pressure applies towards first needle 33 along the direction that makes progress.And in each figure of Figure 15 and 17, line D represents the pressure of valve chamber back pressure chamber 55, and this pressure applies towards first needle 33 along downward direction.Under the situation of Figure 17, when line D and line E were close to each other, the pressure (line E) of the first control valve chamber 54 increased repeatedly and reduces, and the motion of needle 33 (line B) becomes oscillatory movement.On the contrary, in Figure 15, with among Figure 17 by comparison, (line B) is more stable in the motion of needle 33, and the fluctuation of pressure (line E) of the first control valve chamber 54 is subjected to the restriction of continuous connecting passage 68.The wearing and tearing of variation in therefore, can fuel limitation spraying and the valve seat that caused by vibration.
(the 5th and the 6th embodiment)
Continuously the position of connecting passage 68 be not limited among the 4th embodiment like that, but can change on any other correct position, this passage 68 is communicated with first control valve chamber 54 and high-pressure channel 61.In the 5th embodiment of Figure 18, continuously connecting passage 68 is provided among the valve body 33a of first needle 33 the excircle annulus 333 and the first control valve chamber 54 directly is communicated with.The first control valve chamber 54 receives the fuel under high pressure of prearranging quatitys via the hole 681 that is provided in the continuous connecting passage 68 from excircle annulus 333, and wherein this annulus 333 is communicated with high-pressure channel 61 all the time by high pressure affluent channel 64.In the 6th embodiment of Figure 19, connecting passage 68 is communicated with high pressure affluent channel 64 and nozzle needle back pressure chamber 53 continuously.Use this structure, nozzle needle back pressure chamber 53 is connected on the first control valve chamber 54 via the hole 631 that is provided in the communication passage 63.
Even in the 5th and the 6th embodiment, also similar with the 4th embodiment, thus can limit the vibration that first pressure surge of control in the valve chamber 54 limits first needle 33.In the 6th embodiment, structure is similar with second embodiment substantially.Via the unlatching and the closing speed of the valve of adjusting first needle 33, by variation that reduces the fuel injection and the wearing and tearing that limit valve seat, the minimizing of toxic emission can realize in the life time that prolongs sparger.The internal diameter that mensuration is provided in the hole 681 of the continuous connecting passage 68 among the 4th to the 6th embodiment is connected with the internal diameter in hole 651, and this hole 651 is provided in and is used to be communicated with first control valve chamber 54 and the low pressure affluent channel 65 on the downstream side of port 65a.In the 6th embodiment, the internal diameter of measuring hole 681 is connected with the internal diameter in hole 631, and this hole 631 is provided in and is used to connect nozzle needle back pressure chamber 53 in the communication passage 63.
(the 7th embodiment)
Leak with reference to the conversion of Figure 20 description control valve below.In the above-described embodiment, leaked fuel is supplied with the solenoid chamber 57 that wherein accommodates armature 37 from the second control valve chamber 56 via the sliding space of second needle 36.Thereby set leak to recover passage be communicated with solenoid chamber 57 and low-pressure channel 62 restrictions by leaked fuel in solenoid chamber 57 accumulation and the increase of high pressure in the solenoid chamber 57 that causes.For example, the low-pressure channel 262 that is connected on the low-pressure channel 62 in first valve body, 23 upper ends is provided in the excircle part of second valve body 26.Low-pressure channel 262 is communicated with solenoid chamber 57 via the low-pressure channel 263 that is provided in second valve body 26, thereby recovers the leaked fuel in the solenoid chamber 57.Use this structure, when armature 37 attracted on the solenoid 121, second needle 36 lifted with armature 37.Therefore, back pressure chamber 55 is at first sewed, and first needle 33 lifts after second needle 36 has promoted the relatively short time then.Therefore, the fuel that is arranged in the nozzle needle back pressure chamber 53 of first needle, 33 belows leaks (the hereinafter this fuel leak that takes place when the opening of valves is known as " conversion is leaked ") via communication passage 63.
Time difference between the lifting of the lifting of armature 37 and first needle 33 is very little, and like this, the fuel of the fuel of valve back pressure chamber 55 and nozzle needle back pressure chamber 53 is supplied with solenoid chamber 57 (referring to the arrow among the figure) substantially simultaneously.Therefore, pressure surge that produces in solenoid chamber 57 and the hydraulic pressure that is applied to armature 37 change.When the valve closing speed of the valve body 33a in being provided in first needle, 33 lower ends changed owing to the variation that is applied to the hydraulic pressure on the armature 37, fuel injection amount will change.Especially, being used in the short time cycle, spraying under the situation that the examination of fuel is sprayed several times, considerable influence is just arranged.For example, the conversion that is caused by the previous injection fluctuation of leaking can cause the variation of the opening of valves speed in next the injection.Present embodiment has solved above-mentioned shortcoming and has improved the practical application of sparger.
Figure 21 has shown the sparger according to seventh embodiment of the invention.In this embodiment, change has taken place in the part of the structure of first embodiment's sparger, and with the similar parts of first embodiment by identical numeral.In the following description, will parts different with first embodiment in the emitter construction be described mainly.
In the excircle of second valve body 26, set the low-pressure channel 262 that is communicated with low-pressure channel 62 in first valve body, 23 upper ends.In second valve body 26, in the diapire of solenoid chamber 57, opened an end of low-pressure channel 263, and another end of low-pressure channel 263 is opened in the external peripheral surface of second valve body 26 so that be communicated with low-pressure channel 262.Safety check 8 is provided in the connecting end of low-pressure channel 263, and this low-pressure channel 263 is connected on the low-pressure channel 262.Safety check 8 only allows from solenoid chamber 57 to the fuel stream of low-pressure channel 62.Shown in Figure 22 A, safety check 8 comprises valve body 81 and spring 82.Valve body 81 is opened and closed low passage 263.Spring 82 radially is arranged in the step pushing valve body 81 that is used for outside the valve body 81 towards being provided in low-pressure channel 263.Thereby the spring force of spring 82 is set to relatively low value allows valve body 81 to open under predetermined low pressure.Hole 83 forms in valve body 81 so that be communicated with low-pressure channel 262 and low-pressure channel 263 continuously.
Use this structure, when leaking when changing, the fuel of the fuel of valve back pressure chamber 55 and nozzle needle back pressure chamber 53 is supplied with low-pressure channel 262 substantially simultaneously.Yet, since the existence of safety check 8, only a spot of fuel supply low-pressure channel 263 (referring to the arrow among the figure) through via hole 83.Therefore, sizable pressure surge can not take place, and therefore can limit the variation of the valve closing speed that causes owing to the variation that is applied to the hydraulic pressure on the armature 37 in solenoid chamber 57.Even under the situation that the examination that is used for spraying this fuel in the short time cycle is sprayed, also can limit the variation that fuel injection amount occurs therefore.Therefore, improved the controllability that fuel sprays.
On the contrary, shown in Figure 22 B, when the pressure that makes solenoid chamber 57 owing to leaked fuel increases, thereby valve body 81 is opened the pressure that unclasps solenoid chamber 57 against the pushing force of spring 82.The unlatching of valve body 81 and the closed outflow that causes fuel so just may be limited to the pressure surge that is produced when armature 37 promotes.In addition, the leaked fuel that flows into low-pressure section from high-pressure section has reduced, and so just can limit the rising of the temperature of solenoid chamber 57.Like this, just reduced the thermal distortion of parts, so parts can use and have relatively low stable on heating material and make.
Set hole 83 and be used in the air of eliminating after the assembling of sparger in the solenoid chamber 57.In this case, since less relatively from the leakage of slide member generation, so air can be by eliminating air via hole 83 via low-pressure channel 262,263 fuelings from solenoid chamber 57.Yet,, can remove hole 83 not needing to eliminate under the situation of air.
(the 8th embodiment)
The optimum position and the configuration of each master unit of above-mentioned each embodiment are described with reference to Figure 23-25.Figure 23 A is identical with Fig. 2.Figure 23 B is the sectional view that the line XXIIIB in Figure 23 A cuts open, and Figure 23 C is the sectional view that the line XXIIIC-XXIIIC in Figure 23 A cuts open.Figure 23 B has shown the position of high-pressure channel 61 and the position of second needle 36.Shown in Figure 23 B, the central point 36a of the central point 61a of high-pressure channel 61 and second needle 36 arranges that along imaginary line (the level point line that the direction from left to right in Figure 23 B is extended) this line is through the central point 2a of matrix 2.In addition, the high-pressure channel 61 and second needle 36 do not have overlapping each other.More particularly, the high-pressure channel 61 and second needle 36 about central point 2a each other at diametrically opposite.
When second needle 36 was arranged to the central point 2a of matrix 2 biasing, the space that provides along the radially outward of high-pressure channel 61 can maximize.That is, because high-pressure liquid is realized enough intensity through high-pressure channel 61 thereby the conduit wall of high-pressure channel 61 need have enough thickness.The structure of use shown in Figure 23 B, thus can provide relatively large space to allow to provide enough wall thickness so that realize enough intensity round high-pressure channel 61 to high-pressure channel 61.
Figure 23 C has shown the position of high-pressure channel 61 and the position of first needle 33.Shown in Figure 23 C, the central point 33c of the central point 61b of high-pressure channel 61 and first needle 33 arranges that along imaginary line (the level point line that the direction from left to right in Figure 23 C is extended) this line is through the central point 2b of matrix 2.In addition, the high-pressure channel 61 and first needle 33 do not have overlapping each other.More particularly, the high-pressure channel 61 and first needle 33 about central point 2b each other at diametrically opposite.
With Figure 23 category-B seemingly, the space maximization that the radially outward to high-pressure channel 61 is provided.Therefore, provide bigger space round the high-pressure channel 61 of conduction high-pressure liquid, thereby and the wall thickness of high-pressure channel 61 can form the fully big intensity that improves high-pressure channel 61.
The center of center of nozzle needle 31 (Fig. 1) and matrix 2 should be consistent each other.The internal diameter (perhaps flowing out flow velocity) that is equal to, or greater than sidewise hole 332 preferably is arranged to have in the hole 661 that provides in the communication passage 66 between the valve back pressure chamber 55 and the second control valve chamber 56, and wherein this sidewise hole 332 is with high-pressure fuel valve back pressure chamber 55.That is, preferably satisfy following conditions:
The diameter (influx) of the diameter in hole 661 (outflow) 〉=sidewise hole 332.
Like this, via the energising of solenoid 121 when the direction that makes progress moves second needle 36 pressure of valve back pressure chamber 55 can reduce reliably.
As shown in figure 24, represent by " D1 " by the diameter of 33 unlatchings of first needle and the port 65a of closure, and the diameter in the hole 651 of contiguous port 65a is represented by " D2 " on the downstream side of port 65a.In addition, the height of first needle 33 is represented by " H " when first needle 33 promotes.With reference to the symbol of top, (π * D1 * H) is arranged to the cross sectional area (π/4 * D2 * D2) greater than hole 651 to the surface area that is defined by the rear surface 334 and the port 65a of first needle 33.
That is, should satisfy following two conditions:
The surface area of the cross sectional area in hole 651＜define by rear surface 334 and port 65a; And
The diameter D1 of the diameter D2＜port 65a in hole 651.
When first needle 33 when lower valve base 541 lifts, fuel equally flows shown in the arrow among Figure 24.At this moment, during being provided with above having realized, the little gap (lifting height H) between first needle 33 and the port 65a becomes greater than hole 651, so just can not produce the flow resistance of sizable interference liquid stream.
As shown in figure 25, the external diameter of the valve body 33a of first needle 33 is arranged to the diameter D3 greater than vertical hole 231, and its middle shaft part 33b is vertically sliding in the hole 231.That is, should satisfy following conditions:
The diameter D3 in the external diameter of valve body 33a＞vertical hole 231.
Contact vertical hole 231 of first valve body 23 slidably via axial region 33b as first needle 33 of movable link.When having realized being provided with of top, the conical surface 33d of the valve body 33a of first needle 33 engages with angle, the lower end 231a in vertical hole 231.That is, can limit the lifting of first needle 33 by first valve body 23.
In addition, when the diameter in the hole 631 in the communication passage 63 that is connected on the nozzle needle back pressure chamber 53 is provided was represented by D4, (π * D3 * H) was set to the cross sectional area (π/4 * D4 * D4) greater than hole 631 to the surface area that is defined by angle 231a and conical surface 33d.
When first needle 33 when upper valve base 542 lifts, fuel equally flows shown in the arrow among Figure 25.At this moment, the hole 631 with minimum cross sectional area is provided in the communication passage 63, wherein, compares with the flow channel of the more accurate processing of being defined by vertical hole 231 and valve body 33a of needs, and the processing of communication passage 63 is easy to controlled.Like this, the variation that can reduce to make.
The cross sectional area in the hole 631 of Figure 24 (π/4 * D4 * D4) and the cross sectional area in hole 651 (relation between the π/4 * D2 * D2) is according to following setting:
The cross sectional area in the cross sectional area＜hole 631 in hole 651.
Like this, the pressure of nozzle needle back pressure chamber 53 (Figure 23) is pushed the speed and pressure reduces speed and can be provided with individually by hole 631 and hole 651.
As shown in figure 25, owing to making the pressure of nozzle needle back pressure chamber 53, the high-pressure liquid of supplying with high-pressure channel 61 to nozzle needle back pressure chamber 53 via hole 631 increases.On the contrary, as shown in figure 24, when reducing the pressure of nozzle needle back pressure chamber 53, fluid is discharged to low-pressure channel 62 from nozzle needle back pressure chamber 53 via hole 631 and hole 651.Therefore, when the cross sectional area in hole 631 during fully greater than the cross sectional area in hole 651, reducing speed at fluid pressure of nozzle needle back pressure chamber 53 when nozzle needle back pressure chamber 53 is discharged can only be provided with by the cross sectional area that hole 651 is set.On the contrary, can be provided with by the cross sectional area that hole 631 only is set pushing the speed of pressure when nozzle needle back pressure chamber 53 is supplied with fluid.
In Figure 23 A, push the preload of helical spring 34,38 of first needle 33 and armature 37 and the preload (Fig. 1) of helical spring 32 of pushing nozzle needle 31 respectively and be arranged to reduce in the following sequence:
This is owing to following reason.At first, helical spring 32 has defined the valve closing speed of nozzle needle, and helical spring 32 needs maximum preload like this.That is, when pilot jet nozzle needle 31 closed, the pressure of the pressure of nozzle box 51 and nozzle needle back pressure chamber 53 is consistent each other substantially, and the pressure receiving area of the pressure receiving area of nozzle box 51 and nozzle needle back pressure chamber 53 is consistent substantially each other.Therefore, the power that produces by the pressure of nozzle box 51 and balance each other substantially by the power that the pressure of nozzle needle back pressure chamber 53 produces.Therefore, the valve closing speed of nozzle needle is set based on the pushing force of helical spring 32.
Next, helical spring 38 need have preload, and this preload is against the high-pressure liquid close port 66a that imposes on port 66a.At this, the diameter of port 66a is by " D5 " expression, and the hydrodynamic pressure that imposes on port 66a is represented by " P " (for example 200MPa).In this case, helical spring 38 required preloads are expressed from the next:
Preload＞the π of helical spring 38/4 * D5 * D5 * P+ α, wherein α is the extra power that is used for compensating error etc.
π/4 * D3 * D3 * P1+ spring preload
Wherein D3 is that diameter and the P1 of axial region 33b are the pressure of valve back pressure chamber 55.The pushing force that is used for upwards pushing first needle 33 can be expressed as:
π/4×(D3×D3-D1×D1)×P2
Wherein D1 is that diameter and the P2 of port 65a are the pressure of the first control valve chamber 54, and D3＞D1, P1=P2.Therefore, be applied to hydraulic pressure balance substantially on first needle 33.
For a person skilled in the art, the advantage that can form other at an easy rate its modification of Xingqi of going forward side by side.Therefore from broadly of the present invention, that the present invention is not limited to is concrete detailed, the illustrative example of typical equipment and demonstration and description.
Claims (6)
1. sparger comprises:
Elongated matrix (2,2A, 2B, 2C);
Spray-hole (52), its penetrate matrix (2,2A, 2B, wall 2C) is so that burner oil;
Nozzle box (51), its matrix (2,2A, 2B 2C) directly is communicated with spray-hole (52) on the upstream side of the spray-hole in (52), and is supplied to pressurized fuel;
Nozzle needle (31), it is arranged in nozzle box (51) and is driven and is used for allowing or forbids spraying via the fuel of spray-hole (52);
Nozzle needle back pressure chamber (53), its with matrix (2,2A, 2B, 2C) nozzle needle in (31) thus the contiguous place of pedestal end be formed and be supplied to pressurized fuel and apply the back pressure that is used for to the nozzle needle (31) of spray-hole (52) pushing nozzle needle (31);
Release channel, its matrix (2,2A, 2B forms so that discharge the pressure of nozzle needle back pressure chamber (53) to outside low pressure source (3) in 2C);
Control valve chamber (54), its be positioned at matrix (2,2A, 2B is in the intermediate portion of release channel 2C);
First control valve (33), it is arranged in control valve chamber (54) and is actuated to connect between nozzle needle back pressure chamber (53) and low pressure source (3) or disconnect; And
Be used to drive the valve drive (12) of first control valve (33), wherein valve drive (12) is hydrovalve drive unit (12), and it comprises:
Hydraulic channel (61,64,333,332,331,55,66,56,62), its matrix (2,2A, 2B, form 2C), therefore, hydraulic channel (61,64,333,332,331,55,66,56,62) be supplied to pressurized fuel and apply pressurized fuel as being used to drive the control hydraulic fluid of first control valve (33) to first control valve (33);
Second control valve (35), it is actuated to control the fuel flow rate in the hydraulic channel (61,64,333,332,331,55,66,56,62); And
Drive the actuator (121) of second control valve (35).
2. sparger as claimed in claim 1 is characterized in that:
Control valve chamber (54) is formed as the first control valve chamber;
Hydraulic channel (61,64,333,332,331,55,66,56,62) comprising:
The valve back pressure chamber, it is close to the back pressure that the place formed and applied first control valve (33) at the pedestal end with first control valve (33); And
The second control valve chamber, it forms on the downstream side of valve back pressure chamber and holds second control valve (35); And
Second control valve (35) is actuated at the valve back pressure chamber and is positioned at hydraulic channel (61,64,352,331,55,66, connect between the low pressure source (3) on the downstream side of the valve back pressure chamber 56,62) and disconnect, the pressure of valve back pressure chamber reduces respectively and increases thus.
3. sparger as claimed in claim 2 is characterized in that:
Port (65a) be provided at matrix (2,2A, 2B is 2C) in first control room (54) in;
Port (65a) is communicated with low pressure source (3) and opens by this way in the wall of first control room (54), and promptly port (66a) is relative on the movement direction of first control valve (33) with first control valve (33);
First control valve (33) close port (66a) is so that increase the pressure of valve back pressure chamber; And
Restriction (651) matrix (2,2A, 2B, 2C) vicinity of the port (66a) on the downstream side of the port in (66a) is formed.
4. sparger as claimed in claim 1 is characterized in that:
Matrix (2B) comprises fuel feed passage, and this passage is supplied with pressurized fuel along the axial direction extension of matrix (2B) and to nozzle box (51);
The expansion section, cross section (58,711) of in fuel feed passage, making thus form the accumulation chamber, the pressure drop of limits nozzle chamber (51) during, this accumulation chamber via spray-hole (52) burner oil;
Matrix (2B) comprises distal portions (7a) and base ends branch (7b), and the imaginary line that they transversely cross the accumulation chamber is separated and links together by diffusion-bonded;
Distal portions (7a) has the hole (71a) of a part that forms fuel feed passage;
Base ends (7b) has the hole (71b) of the another part that forms fuel feed passage;
Cross sectional area one of at least in the hole (71a) of distal portion (7a) and the hole (71b) of base ends (7b) along predetermined shaft to expanded range, so that form expansion section, cross section (58,711) and thus form the accumulation chamber, wherein this axial range originates in the joint end face between distal portions (7a) and the base ends (7b).
5. sparger as claimed in claim 1 is characterized in that:
Matrix (2C) comprises fuel feed passage, and this passage is supplied with pressurized fuel to nozzle box (51); And
Fuel feed passage is connected to each other via that form in matrix (2C) and communication passage (64,68) that have restriction (681) all the time with the control valve chamber (54) that holds first control valve (33).
6. sparger as claimed in claim 1 is characterized in that:
Second control valve (35) is provided with armature (37), wherein armature (37) be contained in be formed at matrix (2,2A, 2B 2C) integrally moves in the receiving chamber in (57) and with second control valve (35);
Actuator (121) is solenoid (121), and it attracts armature (37) at solenoid (121) when switching on;
Passage (263,262) be set in place matrix between receiving chamber (57) and release channel (2,2A, 2B, 2C) in and hold safety check (8);
When the pressure of receiving chamber (57) surpasses predetermined low pressure, safety check (8) thus open the pressure that discharges receiving chamber (57); And
Safety check (8) restriction flows into the fuel flow rate of receiving chamber (57) via it.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004135371 | 2004-04-30 | ||
| JP135371/2004 | 2004-04-30 | ||
| JP020904/2005 | 2005-01-28 | ||
| JP040730/2005 | 2005-02-17 | ||
| JP067272/2005 | 2005-03-10 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1693696A CN1693696A (en) | 2005-11-09 |
| CN100368679C true CN100368679C (en) | 2008-02-13 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100668682A Expired - Fee Related CN100368679C (en) | 2004-04-30 | 2005-04-29 | Injector having structure for controlling nozzle needle |
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| Country | Link |
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| CN (1) | CN100368679C (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2438035C2 (en) * | 2006-03-03 | 2011-12-27 | Ганзер-Хюдромаг Аг | Injection fuel valve for internal combustion engine (versions) |
| ATE537352T1 (en) * | 2009-06-15 | 2011-12-15 | Delphi Tech Holding Sarl | FUEL INJECTOR |
| DK177456B1 (en) * | 2011-06-27 | 2013-06-17 | Man Diesel & Turbo Deutschland | A fuel valve for large turbocharged two stroke diesel engines |
| US8794547B2 (en) * | 2012-05-15 | 2014-08-05 | Stolle Machinery Company, Llc | Smart solenoid compound gun driver and automatic calibration method |
| FR3042822B1 (en) * | 2015-10-23 | 2017-12-22 | Delphi Int Operations Luxembourg Sarl | FUEL INJECTOR |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0849620A (en) * | 1994-05-30 | 1996-02-20 | Nippondenso Co Ltd | Fuel injection device |
| CN1127024A (en) * | 1993-07-15 | 1996-07-17 | 罗伯特·博施有限公司 | Fuel-injection pump |
| CN1364221A (en) * | 2000-03-15 | 2002-08-14 | 罗伯特·博施有限公司 | Injection device comprising actuator for controlling needle stroke |
| CN1391636A (en) * | 2000-01-13 | 2003-01-15 | 罗伯特·博施有限公司 | Control valve for injector in fuel injection system for IC engine with pressure amplification in control chamber |
-
2005
- 2005-04-29 CN CNB2005100668682A patent/CN100368679C/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1127024A (en) * | 1993-07-15 | 1996-07-17 | 罗伯特·博施有限公司 | Fuel-injection pump |
| JPH0849620A (en) * | 1994-05-30 | 1996-02-20 | Nippondenso Co Ltd | Fuel injection device |
| CN1391636A (en) * | 2000-01-13 | 2003-01-15 | 罗伯特·博施有限公司 | Control valve for injector in fuel injection system for IC engine with pressure amplification in control chamber |
| CN1364221A (en) * | 2000-03-15 | 2002-08-14 | 罗伯特·博施有限公司 | Injection device comprising actuator for controlling needle stroke |
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| CN1693696A (en) | 2005-11-09 |
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Granted publication date: 20080213 Termination date: 20120429 |