CN102828874B

CN102828874B - Solenoid valve and high-pressure pump having same

Info

Publication number: CN102828874B
Application number: CN201210194071.0A
Authority: CN
Inventors: 宫本裕; 三俣直树
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2011-06-13
Filing date: 2012-06-13
Publication date: 2015-04-08
Anticipated expiration: 2032-06-13
Also published as: JP2013002459A; JP5502806B2; CN102828874A; DE102012105085A1

Abstract

A valve-closing direction having a drive direction for urging a valve element (32) against a receiving portion (316) is the same as a counter direction of attraction, which is a drive direction for urging second springs (43A, 43B) of a movable core (53) and rods (41, 42). When the excitation of the coil (51) is switched off, the movable core (53) and the rods (41, 42) can move along the counter-attraction direction by an urging force of the second spring, while a valve element (32 ) moves along the valve-closing direction by an urging force of the first spring (33).

Description

Solenoid valve and the high-pressure service pump with this solenoid valve

Technical field

The present invention relates to solenoid valve and the high-pressure service pump with this solenoid valve.

Background technique

The fuel facility supplying fuel to internal-combustion engine is equipped with the high-pressure service pump of pumping fuel under high pressure.Usually, by piston in response to the to-and-fro motion repeated admission stroke of engine revolution, metering stroke and the circulation (stroke cycle of compression stroke, stroke cycle), high-pressure service pump pressurizes to the fuel extracted out from fuel tank and the fuel of pressurization is delivered to the common rail being connected to Fuelinjection nozzle.

In order to set up this stroke cycle, what solenoid valve (it opens or closes in response to reciprocating motion of the pistons) was used as high-pressure service pump enters valve.Especially, in the intake stroke, valve extraction fuel is entered in the period that moves downward of piston by opening.Subsequently in metering stroke, when piston upwards is to neutral position, enters valve and be opened thus a part of fuel returned its upstream side (fuel source) and metering fuel by this.Subsequently in compression stroke, enter valve and close, the motion and piston keeps up thus compressed fuel and then discharge fuel.By the metering (it is in response to the fuel duty needed for motor) regulating the conversion opportunity from metering stroke to compression stroke to complete fuel.

Usually, the solenoid valve for high-pressure service pump is divided into two types (i.e. open type and normal close type), and this depends on that valve opens the relation of to cut out with valve relative to coil electricity and coil blackout.

In the high-pressure service pump of solenoid valve being equipped with open type, carry out aspirating stroke and metering stroke when coil blackout, and fuel is compressed and is discharged when coil electricity.

In the high-pressure service pump of solenoid valve being equipped with normal close type, carry out aspirating stroke and metering stroke when coil electricity, and fuel is compressed and is discharged when coil blackout.

Such as, corresponding to US2010/0111734A1 for JP2010-106947A() high-pressure service pump in normal-closed electromagnetic valve in, piston rod and anchor (the two corresponds respectively to below by the valve element of the disclosure of invention that describes and mobile core) are integrally formed.When coil blackout, spring members promotes anchor away from the first core (fixed core corresponding to the disclosure of invention).By this, the piston rod integrally formed with anchor is placed in valve closed condition, wherein the valve portion that the enters contact base portion of piston rod.

For JP2010-106947A(correspond to US2010/0111734A1) high-pressure service pump solenoid valve in, mobile core and valve element integrally formed, the weight of the configured in one piece of such mobile core and valve element adds, and by this when coil blackout the mass motion speed of mobile core and valve element reduce.Therefore, valve cuts out the response period and extends, and this period is from exporting the time point of energising shutdown command to solenoid valve to the time point of valve closing movement completing solenoid valve.That is, valve cuts out response poorly.Until complete the time point of the valve closing movement of solenoid valve, the fuel of pressurized chamber just returns upstream side in response to moving upward of piston, and reduces fuel-pumping amount by this.Therefore, when needing large discharge fuel when rotary engine at high speed, become shortage from the fuel duty needed for the fuel-pumping amount opposite engine of high-pressure service pump pumping.

In addition, for the object described, present hypothesis solenoid valve is the solenoid valve of normal close type, it is built as and arranges mobile core and valve element independently, and the push mechanism of mobile core (promotion instrument) along pushing direction (namely mobile core the suction direction that attracts by electromagnetic attraction) promote mobile core, and this pushing direction is the opposite direction (valve opening direction) contrary with the valve closing direction of valve element.When opening valve element when coil electricity, this structure has superiority.But when coil blackout, valve element and mobile core need the thrust of the push mechanism (promotion instrument) resisting mobile core along the mass motion of valve closing direction.In other words, when valve element is closed, the weight of mobile core becomes load, and the gross weight comprising the removable configuration of valve element undesirably increases.Therefore, the movement velocity comprising the removable configuration of valve element reduces when coil blackout, and therefore the valve closedown response period of valve element adversely extends.Therefore, above-mentioned JP2010-106947A(correspond to US2010/0111734A1) solenoid valve when, this structure may cause the shortage of fuel-pumping amount.

Summary of the invention

The disclosure of invention has considered above-mentioned viewpoint.An object of the present invention is to provide a kind of solenoid valve, realize better valve when coil blackout and close response.In addition, another object of the present invention is to provide the high-pressure service pump with this solenoid valve.

According to the disclosure of invention, provide a kind of solenoid valve, comprise valve element, base member, the first push mechanism, coil, stator core, mobile core, bar and the second push mechanism.Valve element is suitable for to-and-fro motion.Base member comprises base portion.Valve element can be seated against in base portion along valve closing direction and can to lift away from described base portion along valve opening direction.Described valve element is pushed against in described base portion along described valve closing direction by the first push mechanism.Coil comprises the wire of winding.Stator core produces magnetic attraction when the coil is energized.When applying magnetic attraction between stator core and mobile core, mobile core is suitable for moving along suction direction.Described bar is fixed on mobile core thus moves with mobile core one.When integrally moving along suction direction in response to the described bar of energising of coil and mobile core, an end of this bar contact valve element and promote valve element along valve opening direction.Second push mechanism promotes mobile core and bar along the back suction force direction contrary with suction direction.Valve closing direction (namely for promoting the pushing direction of the first push mechanism of valve element) and back suction force direction (namely for promoting the pushing direction of mobile core and the second push mechanism of bar) are identical.When disconnecting the energising of coil, mobile core and bar move along back suction force direction by the thrust of the second push mechanism, and valve element moves along valve closing direction by the thrust of the first push mechanism simultaneously.

Accompanying drawing explanation

Accompanying drawing is herein only exemplary but not limits the scope of the disclosure of invention in every way.

Fig. 1 is the schematic sectional view of the high-pressure service pump of the first embodiment according to the disclosure of invention;

Fig. 2 is the sectional view of the valve closed condition of the solenoid valve of the high-pressure service pump that Fig. 1 is shown;

Fig. 3 is the sectional view of the valve open mode of the solenoid valve of the high-pressure service pump that Fig. 1 is shown;

Fig. 4 A illustrates the amplification sectional view of a structure part of Fig. 2;

Fig. 4 B illustrates the amplification sectional view of a structure part of Fig. 3;

Fig. 5 A-5E is the chart of the roadability of the high-pressure service pump that the first embodiment is shown;

Fig. 6 is the chart of the valve closedown responsiveness of valve closedown responsiveness (responsiveness) of the solenoid valve that the first embodiment is shown and the solenoid valve of a comparative example;

Fig. 7 is the schematic sectional view of the high-pressure service pump of the second embodiment according to the disclosure of invention;

Fig. 8 is the schematic sectional view of the high-pressure service pump of a comparative example;

Fig. 9 A-9E is the chart of the roadability of the high-pressure service pump that a comparative example is shown.

Embodiment

The different embodiments of the disclosure of invention are described with reference to the accompanying drawings.

(the first embodiment)

With reference to Fig. 1, what the solenoid valve of the first embodiment of the disclosure of invention was used as high-pressure service pump 10 enters control valve unit 30A.High-pressure service pump 10 is used in the common rail fuel injection device of the diesel engine of Motor Vehicle.Common rail fuel injection device comprises fuel tank, high-pressure service pump 10, common rail (not shown) and Fuelinjection nozzle (not shown).

High-pressure service pump 10 is to the fuel pressurization of the usual pressure extracted out from fuel tank, and the fuel of pressurization is supplied to common rail by high-pressure service pump 10.The fuel under high pressure that common rail accumulation supplies from high-pressure service pump 10, and the fuel under high pressure within it accumulated is respectively allocated to the Fuelinjection nozzle being arranged at each cylinder of motor by common rail.The fuel under high pressure of distribution is sprayed into the firing chamber of respective cylinder by each Fuelinjection nozzle.

The pump case 11 of high-pressure service pump 10 comprises cam shell 70, bearing cap 75 and valve chest 12.

Cam shell 70 and bearing cap 75 are received live axle 80 and are formed the front configuration (pre-pumping arrangement) of pumping and pumping configuration (pumping arrangement).The front configuration of pumping comprises transfer pump (feed pump) 72 and pumping configuration comprises cam 83 and piston 13.

Valve chest 12 is received and is entered control valve unit 30A in the valve receiving opening 16 of valve chest 12.The outer wall in the pipe portion 18 of valve chest 12 is inserted in the receiving opening 77 of the cam shell 70 be communicated with cam chamber 71.Cylinder (piston slip hole) 14 to be formed in pipe portion 18 thus with make piston 13 can in cylinder 14 reciprocating mode support piston 13 within it.Pressurized chamber 95 is formed at by the inwall of the cylinder 14 in pipe portion 18, the axial end of piston 13 and enters in space that the base member 31 of control valve unit 30A and valve element 32 limit.

Valve chest 12 corresponds to the housing of the disclosure of invention.

Supported hole 76 be formed in cam shell 70 with bearing cap 75 is axially inserted and support by supported hole 76, and supported hole 76 is communicated with cam chamber 71.

Bearing cap 75 fixed part (as screw, one is in FIG by shown in dotted line) is fixed on cam shell 70.Gap between the driving force input part 81 of bearing cap 75 and transmission shaft 80 seal by oil sealing 89.

Clutch shaft bearing cover 86 is press-fitted in bearing cap 75 firmly, and make clutch shaft bearing cover 86 rotatably support drive power input part 81, it is an end (upper end portion in Fig. 1) of live axle 80.Second bearing housing 87 is press-fitted in cam shell 70 firmly, makes the second bearing housing 87 rotatably support transfer pump drive portion 82, and it is the other end (underpart in Fig. 1) of live axle 80.When bearing cap 75 is fixed in cam shell 70, clutch shaft bearing cover 86 and the second bearing housing 87 coaxially arrange.

Live axle 80 comprises driving force input part 81, transfer pump drive portion 82 and cam 83.Cam 83 to be formed between driving force input part 81 and transfer pump drive portion 82 and to be accepted in the cam chamber 71 of cam shell 70.Cam 83 is constructed to circular contour.The eccentric shaft 83j of the cam 83 and central shaft 80j of driving force input part 81 and transfer pump drive portion 82 is eccentric.

Transfer pump 72 directly or is indirectly engaged in the transfer pump drive portion 82 of live axle 80 by mating part.

Transfer pump 72 is low pressure supply pumps, and it extracts fuel out and the preliminary fuel pressurization to extracting out from fuel tank.Transfer pump 72 has the pump structure of known pump structure as internal gear pump or wing pump.

Be transferred the fuel of pump 72 initial compression pressure can regulate by pressure regulator (not shown), the usually constant pre-pressure (discharge pressure) of such fuel is kept constant.The transfer the fuel of discharging from transfer pump 72 is supplied to pressurized chamber 95 by the transfer the fuel supply opening 90 of cam shell 70 and the inlet channel 91 of valve chest 12.In addition, a part of transfer the fuel is supplied to cam chamber 71 by the chokes portion (also referred to as restriction, throttled portion) do not described.

The pumping of high-pressure service pump 10 configures the cam 83, piston 13 and the cam ring 84 that comprise live axle 80.Cam ring 84 to be placed between cam 83 and piston 13 and the driving force of live axle 80 is directed at piston 13.Pumping configuration is pressurizeed to the transfer the fuel of discharging from transfer pump 72 further in pressurized chamber 95, and pumping configuration pumping is by the fuel pressurizeed further.

Piston 13 is arranged on the side of cam 83 of live axle 80 along the direction perpendicular to central shaft 80j and eccentric shaft 83j.

Push rod portion 13a is formed at the end of cam 83 side of piston 13, and slidably, slidably contacting part 85 is formed in the outer wall of cam ring 84 along the L-R direction of Fig. 1 to make the relative slidably contacting part 85 of push rod portion 13a.Especially, the end of the push rod portion 13a of piston 13 has plat surface, and the end of the slidably contacting part 85 of cam ring 84 has plat surface, and it is roughly parallel to the plat surface of the 13a end, push rod portion of piston 13.

Cam ring 84 is constructed to polygonal, makes cam ring 84 comprise described plat surface (corresponding to slidably contacting part 85) and arcuate surfaces.The inwall of cam ring 84 is constructed to circle (cylindrical shape).3rd bearing housing 88 is fixed in the inwall of cam ring 84.The cam 83 that 3rd bearing housing 88 is constructed to circle (cylindrical shape) is relatively rotatable.

Piston spring 19 is maintained between the push rod portion 13a of piston 13 and valve chest 12, and piston spring 19 is extended along the axis in pipe portion 18.By this, the push rod portion 13a of piston 13 withstands on the slidably contacting part 85 of cam ring 84 all the time.

The rotation of cam ring 84 is subject to the restriction being applied to the fuel pressure on piston 13 in the thrust of piston spring 19 and pressurized chamber 95.Self non rotating of cam ring 84.But cam ring 84 rotates around the central shaft 80j of live axle 80 and rotates caused cam 83 in response to live axle 80 and moves along the L-R direction in Fig. 1 and move back and forth.

In response to the to-and-fro motion of cam ring 84, piston 13 is along the inwall to-and-fro motion of cylinder 14.In the following description, in order to the object described, piston will be called as moving upward of piston 13 along moving of right direction in Fig. 1, and piston is called as moving downward of piston 13 along moving of left direction in Fig. 1.

When piston 13 moves downward (towards left side motion in Fig. 1), enter control valve unit 30A described in transfer the fuel passes through and be pumped down in pressurized chamber 95 from inlet channel 91.On the contrary, when piston 13 moves upward (towards right side motion in Fig. 1), transfer the fuel is pressurized to the pressure corresponding with the fueling injection pressure of Fuelinjection nozzle in pressurized chamber 95.

One-way valve 68 is arranged in fuel channel 96, and fuel is discharged from pressurized chamber 95 by fuel channel 96.One-way valve 68 limits the discharge fuel return of discharging from pressurized chamber 96 towards common rail and Fuelinjection nozzle in pressurized chamber 95.When pressure opened by the valve that the internal pressure of pressurized chamber 95 exceedes one-way valve 68, pressurized fuel under high pressure to be exported from outlet 98 by outlet passage 97 and is conducted to common rail and Fuelinjection nozzle.

Next, control valve unit 30A and solenoid actuator 50A is entered with reference to Fig. 2-4B description.

Enter valve 30A and comprise base member 31, valve element 32, first spring (promoting instrument as the first push mechanism or first) 33, holding member 34 and plug screw 39.Enter control valve unit 30A and open or close the fuel channel extending to pressurized chamber 95 from inlet channel 91.

Base member 31 is constructed to roughly tubular shape and is placed in the bottom place of the valve receiving opening 16 of valve chest 12.Base member 31 comprises axis hole 311 and multiple intercommunicating pore 313.The central shaft that axis hole 311 is shaped as along base member 31 extends.Each intercommunicating pore 313 is radially connected between the periphery wall 312 of axis hole 311 and base member 31.The space between base 31 and solenoid actuator 50A of valve receiving opening 16 forms fuel bath room (fuel wellchamber) 93.

The surface being placed in the solenoid actuator 50A side of axially side residing for solenoid actuator 50A of base member 31 is constructed to stepped shaft.The end face 314 being positioned at radially inner side of base member 31 forms the spring pedestal of the first spring 33.In addition, plug screw 39 is installed such and screws togather with the female thread being configured as valve receiving opening 16 inner circle wall with the external screw thread making to be configured as plug screw 39 periphery wall in valve chest 12.When base 31 the stepped surfaces 315 being positioned at radial outside promote by plug screw 39 time, base member 31 is pushed against and is fixed on the bottom of valve receiving opening 16.

Taper concave surface base portion 316 is formed around axis hole 311 in the surface of the side, pressurized chamber 95 of base member 31.The valve portion 321 formed in the distal portion of valve element 32 can be seated against in base portion 316.

Valve element 32 is constructed to axle shape (rod), and comprises valve portion 321, medium diameter portion 322 and minor diameter 323, and they are positioned adjacent from side, pressurized chamber 95 vertically.Valve portion 321 has maximum outside diameter and is tapered side contrary with pressurized chamber 95 in the axial direction to be formed tapered portion to correspond to the base portion 316 of base member 31 in valve element 32.

Medium diameter portion 322 is received in the axis hole 311 of base member 31 slidably.Par 325 is formed to provide fuel channel between par 325 and the inner circle wall of axis hole 311 in the peripheral part section of the periphery wall of medium diameter portion 322.

Valve portion 321 in valve element 32 and form neck (limiting unit) 324 between medium diameter portion 322, neck 324 extends continuously from the tapered portion in valve portion 321.Neck 324 forms in the position of the axis hole 311 corresponding to base member 31, makes to form annular pass 92 between neck 324 and the inner circle wall of axis hole 311.

Holding member 34 is such as assemblied in the minor diameter 323 of valve element 32 on the solenoid actuator 50A side of base member 31 by press fit.Stretch out from the end radially outward being positioned at solenoid actuator 50A side of the periphery wall of holding member 34 and form flange 341.First spring 33 is sandwiched between the flange 341 of holding member 34 and the end face 314 of base member 31.Groove 342 is formed to provide fuel channel in the peripheral part of holding member 34.

When holding member 34 is fixed on valve element 32, the movable scope of axis of valve element 32 and holding member 34 is restricted.In addition, when not applying external force to valve element 32, valve element 32 is promoted to make valve portion 321 be seated against in base portion 316 along valve closing direction by the thrust of the first spring 33.

Solenoid actuator 50A comprises coil 51, first stator 52, mobile core 53, second stator 54, flange (the 3rd stator) 55A, bar 41, second spring (promoting instrument as the second push mechanism or second) 43A, stop member 57, spool 58 and pad 59.Flange (the 3rd stator) 55A can be used as the stator core of the disclosure of invention.

Coil 51 is formed by being wound around wire around the spool 58 be formed from a resin.When coil 51 is energized, form magnetic attraction at flange (the 3rd stator) 55A place, and this magnetic attraction is applied between flange 55A and mobile core 53.Therefore, mobile core 53 moves along left direction in Fig. 2-4B.After this object for describing, the left direction in Fig. 2-4B will be called as suction direction, and the right direction in Fig. 2-4B will be called as back suction force direction.

First stator 52, second stator 54 and flange (the 3rd stator) 55A are made up of magnetic material.The axial positions of the first stator 52 on the side contrary with pressurized chamber 95 vertically of flange 55A is placed in the radially inner side of coil 51.Second stator 54 be placed as cover the peripheral part of coil 51 and magnetic force be connected between flange 55A and the first stator 52.

Flange 55A as the 3rd stator is installed in the end contrary with pressurized chamber 95 in the axial direction of valve chest 12.The suction face 551A contrary with pressurized chamber 95 in the axial direction of flange 55A is relative with mobile core 53.Axis hole 552 and spring reception room 553 is formed in flange 55A.Axis hole 552 receives bar 41.Spring reception room 553 in suction face 551A around axis hole 552 opening.

, suppose that the external diameter of the suction face 551A of flange 55A is φ d1 herein, and the diameter of the chamfering opening portion section of spring reception room 553 is φ d2.In this case, magnetic tunnel cross-section area SA, namely the surface area of suction face 551A is expressed by equation (1) below.

SA=π/4 × (φ d1-φ d2) ²equation (1)

The pad 59 be made up of nonmagnetic substance is placed between the first stator 52 and flange 55A.Pad 59 is such as incorporated into the first stator 52 and flange 55A by welding or soldering.Pad 59 has blocked magnetic flux thus has inhibit the magnet short-cut path between the first stator 52 and flange 55A.

Mobile core 53 is made up of magnetic material and is constructed to pipe body.Mobile core 53 to be axially placed between the first stator 52 and flange 55A and to be radially placed on the inner side of the first stator 52 and pad 59.Mobile core 53 is suitable for to-and-fro motion vertically.When coil 51 is energized, mobile core 53 attracts towards the flange 55A as the 3rd stator and therefore moves towards flange.In addition, mobile core 53 has the intercommunicating pore 531 extending axially through mobile core 53.By this, reciprocating time, the pressure on rear side of the pressure on front side of mobile core 53 and mobile core 53 roughly keeps constant by intercommunicating pore 531.

Bar 41 is integrally formed with mobile core 53, more particularly such as by weld, soldering or be fixed by caulking to mobile core 53, thus to be formed and the synergistic armature assembly of mobile core 53 (removable configuration) 40A.Bar 41 is accepted through the axis hole 552 of flange 55A and is suitable for to-and-fro motion together with mobile core 53 vertically.The end be positioned on side, pressurized chamber 95 along suction direction of bar 41 is relative with the end of valve element 32.After this, in order to the object described, armature assembly 40A moves to be called as travel forward along suction direction, and armature assembly 40A moving to be called as and move backward along back suction force direction.

Second spring 43A is accepted in the spring reception room 553 of flange 55A.The bottom surface of the end thereof contacts spring reception room 553 of the second spring 43A, and the other end of the second spring 43A contacts the end face be positioned on side residing for flange 55A of described mobile core 53.Second spring 43A promotes mobile core 53 and bar 41 along back suction force direction.Now, the ends contact of bar 41 is placed on the stop member 57 in the inner bottom part of the first stator 53, thus limits the motion backward of bar 41.

Next, the operation of high-pressure service pump 10 will be described.In high-pressure service pump 10, piston 13 synchronously moves along the L-R direction of Fig. 1 up or down along with the rotation of the cam 83 of live axle 80, the circulation of repeated admission stroke, metering stroke (metering stroke) and compression stroke.

(initial conditions)

When coil 51 is not energized, mobile core 53 is promoted (see Fig. 2) towards stop member 57 by the thrust of the second spring 43A, makes bar 41 contact stops 57.Now, valve element 32 is seated against (see Fig. 2 and 4A) in base portion 316 by the thrust of the first spring 33.

Fuel can flow, to make the fuel pressure of the fuel pressure of annular pass 92 and fuel bath room 93 roughly mutually the same through the fuel channel of the groove 342 of the fuel channel be defined to the par 325 of medium diameter portion 322 and axis hole 311 inner circle wall and holding member 34 between annular pass 92 and fuel bath room 93.

(aspirating stroke)

When the lift of cam 83 starts to reduce in the intake stroke, piston 13 moves downward.By this, pressurized chamber 95 is depressurized thus produces pressure reduction between annular pass 92 and pressurized chamber 95.When the fuel pressure of annular pass 92 increases above the thrust of the first spring 33, valve element 32 starts to leave, and namely lifts away from base portion 316 and the valve therefore starting valve element 32 is opened.

When coil 51 is energized, the electromagnetic attraction be directly proportional to magnetic circuit cross-section area SA is applied between flange 55A and mobile core 53.When magnetic attraction increases above the thrust of the second spring 43A, armature assembly 40A(bar 41 and mobile core 53) start to travel forward, namely rise along suction direction.Subsequently, bar 41 distal contact valve element 32 and promote valve element 32 along valve opening direction.During the energising of coil 51 (current"on"time), valve element 32 is remained on valve open mode (see Fig. 3 and 4B) by bar 41.

Under valve open mode, fuel flows into pressurized chamber 95(see the solid arrow F1 Fig. 4 B from inlet channel 91 through annular energising 92).Part fuel can flow between annular pass 92 and fuel bath room 93 through the fuel channel of the groove 342 of the fuel channel be defined to the par 325 of medium diameter portion 322 and the inner circle wall of axis hole 311 and holding member 34 (shown see the dotted arrow F 2 in Fig. 4 B).By this, the fuel pressure of annular pass 92 and the fuel pressure of fuel bath room 93 become roughly mutually the same, and the fuel lubricated slide part between valve element 32 and base member 31 flowed between annular pass 92 and fuel bath room 93.

(metering stroke)

When the motion of cam 83 to become at lower dead centre (bottom dead center) place move upward thus move up piston 13 time, operate and become metering stroke from aspirating stroke.Now, the energising of keeping coil 51, and valve element 32 is maintained at valve open mode.In response to moving upward of piston 13, the fuel being drawn into pressurized chamber 95 is flow back to annular pass 92 thus metering fuel.

(compression stroke)

When disconnecting the energising of coil 51, the electromagnetic attraction between mobile core 53 and flange 55A just loses.Subsequently, armature assembly 40A moves along back suction force direction by the thrust of the second spring 43A, makes armature assembly 40A return its initial position.Valve element 32 moves along valve closing direction by the thrust of the first spring 33.

Therefore, the discharge of fuel from 95 to annular pass, pressurized chamber 92 is just finished.Subsequently, when in response to piston 13 move upward thus in pressurized chamber 95 pressure increase the valve exceeding one-way valve 68 open pressure time, fuel is discharged (see Fig. 1) from outlet 98 through outlet passage 97.

Herein, the load on spring of the first spring 33 and the load on spring of the second spring 43A are so set to make armature assembly 40A along the movement velocity of back suction force direction higher than the valve closing velocity (movement velocity) of valve element 32 when disconnecting the energising of coil 51.Especially, the thrust of the second spring 43A is set to be greater than the thrust of the first spring 33.

Like this, once lose electromagnetic attraction, armature assembly 40A just moves backward along back suction force direction, and valve element 32 moves along valve closing direction subsequently.Especially, armature assembly 40A and valve element 32 move independently of one another by independently thrust.

Next, undertaken contrasting the advantage describing the embodiment of the present invention by with a comparative example.

Fig. 8 illustrates the solenoid valve of a comparative example, and what it was used as high-pressure service pump enters control valve unit 20C.Enter control valve unit 20C and have valve member 21, it is placed in the space in valve outer body 23 and valve between body 24.The first spring 22 that valve member 21 is accepted in the spring reception room 242 of body 24 in valve promotes, and valve member 21 is seated against in the base portion 231 of valve outer body 23.

In solenoid actuator 50C, the second spring 56 to be placed between the end of needle 61 and stop member 57 and to promote the left direction in needle 61(Fig. 8 along suction direction).The thrust of the second spring 56 is set to be less than the thrust of the first spring 22.Therefore, under the off-position of coil 51, valve member 21 is seated against in base portion 231 not by the impact of the thrust of the second spring 56.

Identical in figs 2 and 3 with the assembly of the solenoid actuator 50C shown in same reference numerals substantially with the solenoid actuator 50A of the first embodiment.

Although different all from the first embodiment of the position of the vibration-direction of piston 13 and inlet channel 911, these different not substantial differences.

When coil 51 is energized, electromagnetic attraction puts between flange 55C and mobile core 53.Then, needle 61 travels forward (left direction in Fig. 8) by the thrust of electromagnetic attraction and the second spring 56 along suction direction.

Enter control valve unit 20C be used in high-pressure service pump when, valve member 21 open by the pressure reduction between the pressure on the pressure on valve member 21 upstream side and valve member 21 downstream side, as in the first embodiment.In addition, even if do not produce pressure reduction between the upstream side and downstream side of valve member 21, when proal needle 61 impels valve member 21 to resist the thrust of the first spring 22, valve member 21 is opened under the thrust of the first spring 22.Therefore, inlet channel 911 and pressurized chamber 95 are communicated with each other by the passage in inside body 24 in valve outer body 23 and valve.

When entering control valve unit 20C for high-pressure service pump, the flange 611 being arranged at needle 61 helps the valve by using the pressure reduction between the upstream side of flange 611 and downstream side to carry out valve member 21 to open.

When disconnecting the energising of coil 51, the electromagnetic attraction putting on mobile core 53 disappears.Under power difference between the thrust and the thrust of the second spring 56 of the first spring 22 acts on, valve member 21 moves along valve closing direction, and such valve member 21 impels needle 61 move (right direction in Fig. 8) along back suction force direction and be seated against in base portion 231.Therefore, valve member 21 needs to carry out extra work (namely having extra work amount): except the valve closing movement needed for it, impel needle 61 to resist the thrust of the second spring 56 when valve cuts out.The impact of this operation of valve member 21 is described with reference to Fig. 9 A-9E.

Fig. 9 A-9E illustrates the operating characteristics entering the solenoid valve of valve being used as high-pressure service pump.Especially, Fig. 9 A illustrates the time dependent chart of the lift of cam.Fig. 9 B illustrates that time dependent chart is ordered in the energising (open, close) of coil.Fig. 9 C illustrates the time dependent chart of the electric current flowed in coil.Fig. 9 D be valve member 21 is shown lift over time (shown in dotted line in Fig. 9 D) and needle 61 lift over time () in Fig. 9 D as shown by the solid line.Fig. 9 E illustrates the time dependent chart of the pump output of fuel.

At time point ta, the lift variation of cam is that cam starts to have moved downward aspirating stroke from upper dead center (TDC).Now, the fuel pressure of pressurized chamber 95 reduces, and like this due to the pressure reduction between the pressure on the side, pressurized chamber of the pressure on upstream passageway 912 side of valve member 21 and valve member 21, valve member 21 moves along its valve opening direction, and valve is opened and completed at moment t2.In addition, at time point t1, open the energising of order (energization ON command) opening coil 51 by energising and produce electromagnetic attraction at solenoid actuator 50C.Subsequently, needle 61 travels forward and arrives the proal limit (full lift) at time point t3.

Arrive lower dead centre (BDC) in the lift of time point tb cam, and aspirating stroke is converted to metering stroke by this.Be energized ON-and OFF-command (energization OFF command) at the electric current of time point t4 arrival maximum value at time point tc stopped, this determines based on required fuel-pumping amount.Subsequently, valve member 21 promotes needle 61 along moving direction backward and closes.When promoting needle 61 load backward and increasing, namely valve cuts out response period TvC(, the time point t5 from the time point tc disconnecting energising closes to the valve completing valve member 21) elongated.Herein, valve cuts out the elongated of response period and is also referred to as the deterioration that valve cuts out response.

After the time point tc disconnecting energising, operation is shown as and becomes compression stroke from metering stroke.But the fuel of pressurized chamber 95 does not turn back to upstream passageway 912 during valve cuts out response period TvC.Therefore pressurization and the discharge (pumping) of fuel is not in fact completed.

Subsequently, carry out discharge and the pressurization of fuel from time point t5, this is after valve cuts out the response period TvC past.But now the position of cam arrives upper dead center, and remaining up stroke is very little.Therefore, the pump output QC of fuel decreases.Therefore, valve cuts out the minimizing that the deterioration responded causes fuel-pumping amount, namely relative to required fuel duty, and the shortage of fuel-pumping amount.

As mentioned above, when the solenoid valve of this comparative example is applied to equipment, need high-speed response, therefore the valve closedown response of solenoid valve becomes and has problem very much.Next, the operating characteristics with the first embodiment with reference to Fig. 5 A-5E contrasts by the operating characteristics of this comparative example.

The parameter of Fig. 5 A-5E and the identical of Fig. 9 A-9E.But it should be noted that with Fig. 9 D unlike, Fig. 5 D illustrate the lift of valve element 32 over time (represented by dashed line in Fig. 5 D) and armature assembly 40A lift over time (indicated by the solid line in Fig. 5 D).In addition, from aspirating stroke to the metering working state of stroke and the roughly the same of this comparative example.Especially, the relative electromagnetic attraction loss of the thrust of the second spring 43A when opening the energising of coil 51, therefore time point t3 trends towards postponing.But this does not have materially affect to the function of high-pressure service pump.

After time point tc disconnects the energising of coil 51 with energising ON-and OFF-command, before the valve closing movement of valve element 32, by means of the thrust of the second spring 43A along back suction force direction (right direction in Fig. 1), armature assembly 40A moves backward along back suction force direction.Then, by the first spring 33 thrust and do not need to drive armature assembly 40A as its load, valve element 32 only moves along valve closing direction.Therefore, the quick valve closing movement of valve element 32 is possible.Therefore, valve cuts out response period TvA can be shortened---from the time point tc of the valve closing movement of open valve element 32 to the time point t5 of valve closing movement completing valve element 32---, and therefore improves valve and close response.

Like this, still there is the enough up strokes to cam top dead, because this increasing the pump output QA of fuel.Therefore, valve can be improved and close response, and suitably can reach the fuel-pumping amount of supply needed for relative fuel.

Fig. 6 illustrates that the valve entering control valve unit 30A of the first embodiment cuts out the chart entering the valve cut out response of control valve unit 20C of response and this comparative example.

As shown in Figure 6, when the load on spring of the load on spring of first spring 33 of the first embodiment and the first spring 22 of comparative example increases, valve cuts out the response period and has been shortened.Such as, suppose that the other factors (weight and move distance as removable configuration) except the first spring is set in the first embodiment all identical with comparing embodiment, the load on spring of the first spring the first embodiment be also identical in comparing embodiment.Like this, with comparative example enter compared with control valve unit 20C, the first embodiment enters control valve unit 30A and can shorten valve and close the response period.

(the second embodiment)

Next, the second embodiment of the disclosure of invention is described with reference to Fig. 7.The identical reference character of the parts identical with the first embodiment represents, repeats no more.

Similar with the first embodiment, what the solenoid valve of the second embodiment was used as high-pressure service pump enters control valve unit 30B.The difference entering control valve unit 30A entering control valve unit 30B and the first embodiment is the position of the shape of bar, the shape of flange and the second spring.

Bar 42 has flange 421, and it stretches out from a part of radially outward being positioned at base member 31 side of flange (as stator core) 55B.The radially outer of the first spring 33 is placed in as the second push mechanism or the second the second spring 43B promoting instrument.The end thereof contacts flange 421 of the second spring 43B, and the end face 314 of the other end of the second spring 43B contact base member 31.Like this, the second spring 43B promotes armature assembly 40B(bar 42 and mobile core 53 along back suction force direction (right direction in Fig. 7)).

In addition, different from the flange 55A of the first embodiment, flange 55B does not need the spring reception room 553 of opening in the suction face of flange 55B.

, suppose that the external diameter of the suction face 551B of flange 55B is φ d3 herein, and the diameter of the chamfering opening portion section of axis hole 552 is φ d4.Like this, magnetic tunnel cross-section area SB, namely the surface area of suction face 551B can be represented by equation (2) below.

SA=π/4 × (φ d1-φ d2) ²equation (2)

When coil 51 is energized, the electromagnetic attraction be directly proportional to magnetic circuit cross-section area SB is applied between flange 55B and mobile core 53.The thrust that armature assembly 40B resists the second spring 43B along suction direction (left direction in Fig. 7) travels forward, and bar 42 promotes valve element 32.Subsequently, valve element 32 resists the pushing motion of the first spring 33 and opens.

When disconnecting the energising of coil 51, the thrust that armature assembly 40B resists the second spring 43B along back suction force direction (right direction in Fig. 7) is moved backward.In addition, valve element 32 to move along valve closing direction by the thrust of the first spring 33 and is seated against in base portion 316.Now, the load on spring of the first spring 33 and the load on spring of the second spring 43B are by the valve closing velocity (movement velocity) so setting to make the movement velocity of armature assembly 40B higher than valve element 32, and namely the motion of armature assembly 40B is prior to the valve closing movement of valve element 32.Like this, be similar to the first embodiment, the valve that may improve valve element 32 cuts out response.

In addition, in a second embodiment, magnetic circuit cross-section area SB is limited by aforesaid equation (2).Therefore, for producing the electromagnetic attraction identical with the first embodiment, magnetic circuit cross-section area SB can be set equal to the magnetic circuit cross-section area SA(of the first embodiment see equation (1)).Therefore, the diameter phi d4 of the chamfering opening portion section of the axis hole 552 of the second embodiment is less than the diameter phi d2 of the first embodiment, because lack spring reception room 553.Therefore, the external diameter φ d3 of suction face 551B is less than the external diameter φ d1 of suction face 551A.Therefore the external diameter of mobile core 53 can be reduced, and can reduce the weight of mobile core 53 by this.Therefore can improve the valve entering control valve unit 30B further and close response.

The improvement to above-described embodiment will be described now.

(A) in the above-described embodiments, the load on spring of the first spring 33 and the load on spring of second spring 43A, 43B are so set to make when disconnecting the energising of coil 51 armature assembly 40A, 40B along the movement velocity of back suction force direction higher than the valve closing velocity (movement velocity) of valve element 32.But the movement velocity of armature assembly 40A, 40B is not necessarily higher than the valve closing velocity of valve element 32.

When the movement velocity of armature assembly 40A, 40B is lower than when lacking the valve closing velocity of valve element 32 of ideal case of armature assembly 40A, 40B, the valve closing velocity of valve element 32 is subject to the restriction of the movement velocity of assembly 40A, 40B.

Even if but in this case, armature assembly 40A, 40B are pushed and move along the direction identical with valve element 32.Therefore, only diminished relative to the speed difference of the valve closing movement of valve element 32.Especially, compared with the comparative example (wherein needle 61 is pushed along the direction that the valve closing direction with valve element 32 is contrary) of Fig. 8, the valve closing movement of valve element 32 is obviously preferred.Therefore, even if in this case, the advantage of the disclosure of invention also can be realized.

(B) enter in control valve unit 30B in the second embodiment, the end contrary with the flange 421 of bar 42 of the second spring 43B contacts the end face 314 of base member 31.The disclosure of invention is not limited thereto.That is, the end contrary with the flange 421 of bar 42 of the second spring 43B can be fixed in any suitable component.Such as, end difference can be formed in the inwall of plug screw, and the end of the second spring 43B can contact this end difference.

(C) in the above-described embodiments, one group of piston 13, enter control valve unit 30A, 30B and solenoid actuator 50A, 50B are arranged in high-pressure service pump 10.But the disclosure of invention is not limited thereto.Many covers (group) piston, enter control valve unit, solenoid actuator can be arranged around live axle in high-pressure service pump.

(D) solenoid actuator of the disclosure of invention is not limited to the high-pressure service pump being applied to diesel engine.Such as, what the solenoid valve of the disclosure of invention can be applicable to petrolic high-pressure service pump enters control valve unit.In addition, the solenoid valve of the disclosure of invention can be applicable to other suitable equipment any as needed the Fuelinjection nozzle of high-speed response.

As mentioned above, the disclosure of invention is not limited to above-described embodiment and improvement thereof.That is, above-described embodiment and improvement thereof can be modified in many ways and not depart from the spirit and scope of the present invention.

Claims

1. a solenoid valve, comprising:

Be suitable for reciprocating valve element (32);

Comprise the base member (31) of base portion (316), wherein said valve element (32) can be seated against described base portion (316) along valve closing direction and goes up and can lift away from described base portion (316) along valve opening direction;

First push mechanism (33), described valve element (32) is pushed against in described base portion (316) along described valve closing direction by it;

Comprise the coil (51) being wound around wire;

Stator core (55A, 55B), it produces magnetic attraction when described coil (51) is energized;

Mobile core (53), it is suitable for moving along suction direction when magnetic attraction puts between described stator core (55A, 55B) and described mobile core (53);

Be fixed on described mobile core (53) thus with the bar (41 that moves of mobile core (53) one, 42), wherein when the described bar (41 of energising in response to coil (51), 42) when integrally moving along suction direction with described mobile core (53), described bar (41,42) contacts an end of described valve element (32) and promotes described valve element (32) along described valve opening direction; And

Second push mechanism (43A, 43B), it promotes described mobile core (53) and described bar (41,42) along the back suction force direction contrary with suction direction, wherein:

Described valve closing direction is identical with described back suction force direction, described valve closing direction is the pushing direction of the first push mechanism (33) for promoting described valve element (32), described back suction force direction is for promoting described mobile core (53) and bar (41,42) pushing direction of the second push mechanism (43A, 43B); And

When disconnecting the energising of coil (51), described mobile core (53) and bar (41,42) by the second push mechanism (43A, thrust 43B) is moved along described back suction force direction, and described valve element (32) is moved along described valve closing direction by the thrust of the first push mechanism (33) simultaneously.

2. solenoid valve according to claim 1, wherein, when disconnecting the energising of coil (51), described mobile core (53) and bar (41,42) are suitable for moving along back suction force direction along the movement velocity that the movement velocity of valve closing direction is high than described valve element (32).

3. solenoid valve according to claim 1, the end thereof contacts stator core (55A) of wherein said second push mechanism (43A), further, the other end contrary with described one end of the second push mechanism (43A) of the second push mechanism (43A) contacts described mobile core (53).

4. solenoid valve according to claim 1, the flange (421) of bar (42) described in the end thereof contacts of wherein said second push mechanism (43B), and the other end contrary with described one end of the second push mechanism (43B) of the second push mechanism (43B) is fixed.

5. a high-pressure service pump, comprising:

Piston (13);

Receive the cylinder (14) of described piston (13), wherein piston (13) is suitable for to-and-fro motion in cylinder (14);

Housing (12), described housing comprises: pressurized chamber (95), and wherein fuel is pressurizeed by piston (13); And supply fuel to the inlet channel (91) of described pressurized chamber (95); And

What comprise the solenoid valve of claim 1-4 any one enters control valve unit (30A, 30B), wherein saidly enter control valve unit (30A, 30B) to-and-fro motion be suitable in response to piston (13) is opened or closed, to make to be communicated with or not to be communicated with between described inlet channel (91) with described pressurized chamber (95).