CN102828874A - Solenoid valve and high-pressure pump having same - Google Patents

Solenoid valve and high-pressure pump having same Download PDF

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Publication number
CN102828874A
CN102828874A CN2012101940710A CN201210194071A CN102828874A CN 102828874 A CN102828874 A CN 102828874A CN 2012101940710 A CN2012101940710 A CN 2012101940710A CN 201210194071 A CN201210194071 A CN 201210194071A CN 102828874 A CN102828874 A CN 102828874A
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China
Prior art keywords
valve
mobile core
fuel
push mechanism
valve element
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Granted
Application number
CN2012101940710A
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Chinese (zh)
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CN102828874B (en
Inventor
宫本裕
三俣直树
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Denso Corp
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Denso Corp
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Publication of CN102828874B publication Critical patent/CN102828874B/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F02M59/367—Pump inlet valves of the check valve type being open when actuated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/464—Inlet valves of the check valve type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)
  • Fuel-Injection Apparatus (AREA)

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 high-pressure service pump with this solenoid valve
Technical field
The present invention relates to solenoid valve and high-pressure service pump with this solenoid valve.
Background technique
The fuel facility that supplies fuel to internal-combustion engine is equipped with the high-pressure service pump of pumping fuel under high pressure.Usually; Through the circulation (stroke cycle of piston in response to to-and-fro motion repeated admission stroke, metering stroke and the compression stroke of engine revolution; Stroke cycle), high-pressure service pump pressurizes to the fuel of extracting out from fuel tank and the fuel of pressurization is delivered to the common rail that is connected in Fuelinjection nozzle.
In order to set up this stroke cycle, solenoid valve (it opens or closes in response to reciprocating motion of the pistons) is used as the entering valve of high-pressure service pump.Especially, in aspirating stroke, during the moving downward of piston, get into valve and extract fuel out through opening.Subsequently in the metering stroke, when piston moves up to the neutral position, be opened a part of fuel is returned its upstream side (fuel source) and metering fuel by this thereby get into valve.Subsequently in compression stroke, get into valve and close, thus and keep up motion compressed fuel and then discharge fuel of piston.Through regulating the metering (it is in response to the required fuel duty of motor) of accomplishing fuel from the conversion opportunity of metering stroke to compression stroke.
Usually, the solenoid valve that is used for high-pressure service pump is divided into two types (being open type and normal close type), and this depends on that valve is opened with valve closes the relation with respect to coil electricity and coil blackout.
In the high-pressure service pump of the solenoid valve that is equipped with open type, when coil blackout, carry out aspirating stroke and metering stroke, and fuel is compressed and discharges when coil electricity.
In the high-pressure service pump of the solenoid valve that is equipped with normal close type, when coil electricity, carry out aspirating stroke and metering stroke, and fuel is compressed and discharges when coil blackout.
For example; In the normal close type solenoid valve of the high-pressure service pump that is used for JP2010-106947A (corresponding to US2010/0111734A1), piston rod and anchor (the two corresponds respectively to below valve element and mobile core with the disclosure of invention of describing) are integrally formed.When coil blackout, spring members promotes anchor away from first core (corresponding to the fixed core of the disclosure of invention).By this, be placed in the valve closed condition, wherein the entering valve portion of piston rod contact pedestal part with the integrally formed piston rod of anchor.
Solenoid valve at the high-pressure service pump that is used for JP2010-106947A (corresponding to US2010/0111734A1); Mobile core and valve element are integrally formed; The weight of the configured in one piece of mobile core and valve element has increased like this, and by this when coil blackout the mass motion speed of mobile core and valve element reduced.Therefore, elongated segment during the valve response closing, this period is the time point from time point to the valve closing movement of accomplishing solenoid valve of output energising shutdown command to solenoid valve.That is to say that the valve response closing is not so good.Up to the time point of the valve closing movement of accomplishing solenoid valve, the fuel of pressurized chamber just returns upstream side in response to moving upward of piston, and reduces the fuel-pumping amount by this.Therefore, when when rotary engine under high rotating speed, needing big flow fuel, from the shortage that becomes of the required fuel duty of the relative motor of fuel-pumping amount of high-pressure service pump pumping.
In addition; Be purpose of description; The hypothesis solenoid valve is the solenoid valve of normal close type now; It is built as mobile core and valve element is set independently, and the push mechanism of mobile core (promotion instrument) promotes mobile core along pushing direction (be removable core by suction direction that electromagnetic attraction attracted), and this pushing direction is the opposite direction (valve open direction) opposite with the valve closing direction of valve element.This structure has superiority when when coil electricity, opening the valve element.But when coil blackout, valve element and mobile core need resist the thrust of push mechanism (promotion instrument) of mobile core along the mass motion of valve closing direction.In other words, when the valve element was closed, the weight of mobile core became load, and comprised that the gross weight of the removable configuration of valve element has increased unfriendly.Therefore, comprise that the movement velocity of the removable configuration of valve element has reduced when coil blackout, so prolonged the valve response closing period of valve element unfriendly.Therefore, under the situation of the solenoid valve of above-mentioned JP2010-106947A (corresponding to US2010/0111734A1), this structure possibly cause the shortage of fuel-pumping amount.
Summary of the invention
The disclosure of invention has been taken all factors into consideration above-mentioned viewpoint.An object of the present invention is to provide a kind of solenoid valve, when coil blackout, realize better valve response closing.In addition, another object of the present invention provides the high-pressure service pump with this solenoid valve.
According to the disclosure of invention, a kind of solenoid valve is provided, comprise valve element, base member, first push mechanism, coil, stator core, mobile core, bar and second push mechanism.The valve element is suitable for to-and-fro motion.Base member comprises pedestal part.But the valve element along valve closing direction seating on pedestal part and can open direction along valve and lift away from said pedestal part.First push mechanism is pushed against said valve element on the said pedestal part along said valve closing direction.Coil comprises the lead of winding.Stator core produces magnetic attraction when coil electricity.Mobile core is suitable for moving along the suction direction when between stator core and mobile core, applying magnetic attraction.Thereby said bar is fixed in mobile core to move with the mobile core one.When in response to the said bar of the energising of coil and mobile core when suction direction one is moved, an end of this bar contact valve element and open direction along valve and promote the valve element.The second push mechanism edge promotes mobile core and bar with suction back suction force direction in the opposite direction.Valve closing direction (promptly being used to promote the pushing direction of first push mechanism of valve element) and back suction force direction (promptly being used to promote the pushing direction of second push mechanism of mobile core and bar) are identical.When breaking off the energising of coil, mobile core and bar move along the back suction force direction by the thrust of second push mechanism, and the valve element moves along the valve closing direction by the thrust of first push mechanism simultaneously.
Description of drawings
The accompanying drawing here is merely exemplary but not limits the scope of the disclosure of invention in every way.
Fig. 1 is the schematic sectional view according to first embodiment's of the disclosure of invention high-pressure service pump;
Fig. 2 is the sectional view of valve closed condition of solenoid valve that the high-pressure service pump of Fig. 1 is shown;
Fig. 3 is the sectional view of valve open mode of solenoid valve that the high-pressure service pump of Fig. 1 is shown;
Fig. 4 A illustrates the amplification sectional view of the structure part of Fig. 2;
Fig. 4 B illustrates the amplification sectional view of the structure part of Fig. 3;
Fig. 5 A-5E is the chart of roadability that first embodiment's high-pressure service pump is shown;
Fig. 6 is the chart of valve response closing degree of solenoid valve of valve response closing degree (responsiveness) and a comparative example that first embodiment's solenoid valve is shown;
Fig. 7 is the schematic sectional view according to second embodiment's of the disclosure of invention high-pressure service pump;
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 roadability that the high-pressure service pump of a comparative example is shown.
Embodiment
With the different embodiments that illustrate and describe the disclosure of invention.
(first embodiment)
With reference to Fig. 1, first embodiment's of the disclosure of invention solenoid valve is used as the entering control valve unit 30A of high-pressure service pump 10.High-pressure service pump 10 is used in the common rail fuel injection device of diesel engine of Motor Vehicle.Common rail fuel injection device comprises fuel tank, high-pressure service pump 10, is total to rail (not shown) and Fuelinjection nozzle (not shown).
10 pairs of fuel pressurizations of high-pressure service pump from the usual pressure of fuel tank extraction, and high-pressure service pump 10 offers common rail with the fuel that pressurizes.Common rail is accumulated the fuel under high pressure of supplying with from high-pressure service pump 10, and the fuel under high pressure that common rail will be accumulated within it is respectively allocated to the Fuelinjection nozzle that is arranged at each cylinder of motor.Each Fuelinjection nozzle sprays into the fuel under high pressure of distributing the firing chamber of respective cylinder.
The pump case 11 of high-pressure service pump 10 comprises cam shell 70, bearing cap 75 and valve chest 12.
Configuration (pre-pumping arrangement) and pumping configuration (pumping arrangement) before cam shell 70 is admitted live axle 80 and formed pumping with bearing cap 75.Configuration comprises that transfer pump (feed pump) 72 and pumping configuration comprise cam 83 and piston 13 before the pumping.
Valve chest 12 is admitted in the valve receiving opening 16 of valve chest 12 and is got into control valve unit 30A.The outer wall of the pipe portion 18 of valve chest 12 is inserted in the receiving opening 77 of the cam shell 70 that is communicated with cam chamber 71.Cylinder (piston slip hole) thus 14 be formed in the pipe portion 18 so that piston 13 can be in cylinder 14 reciprocating mode support piston 13 within it.Pressurized chamber 95 be formed at the axial end of the inwall of the cylinder 14 of pipe portion 18, piston 13 and get into the base member 31 of control valve unit 30A and space that valve element 32 is limited in.
Valve chest 12 is corresponding to the housing of the disclosure of invention.
Supported hole 76 is formed in the cam shell 70 so that bearing cap 75 axially inserts and 76 supports in supported hole, and supported hole 76 is communicated with cam chamber 71.
Bearing cap 75 fixed parts (like screw, one of which in Fig. 1 by shown in the dotted line) are fixed in cam shell 70.Gap between the driving force input part 81 of bearing cap 75 and transmission shaft 80 is sealed by oil sealing 89.
Clutch shaft bearing cover 86 is pressed fit in bearing cap 75 firmly, makes rotatably support drive power input part 81 of clutch shaft bearing cover 86, and it is an end (upper end portion among Fig. 1) of live axle 80.Second bearing housing 87 presses fit in cam shell 70 firmly, makes second bearing housing 87 rotatably support transfer pump drive portion 82, and it is the other end (underpart among Fig. 1) of live axle 80.When bearing cap 75 was fixed in cam shell 70, clutch shaft bearing cover 86 and second bearing housing 87 was coaxially arranged.
Live axle 80 comprises driving force input part 81, transfer pump drive portion 82 and cam 83.Cam 83 is formed between driving force input part 81 and the transfer pump drive portion 82 and is accepted in the cam chamber 71 of cam shell 70.Cam 83 is constructed to circular contour.The central shaft 80j of the eccentric shaft 83j of cam 83 and driving force input part 81 and transfer pump drive portion 82 is eccentric.
Transfer pump 72 directly or indirectly is engaged in the transfer pump drive portion 82 of live axle 80 through mating part.
Transfer pump 72 is low pressure supply pumps, and it extracts fuel and the tentatively fuel pressurization to extracting out out from fuel tank.Transfer pump 72 has the pump structure of known pump structure such as internal gear pump or wing pump.
The pressure that is transferred the fuel of pump 72 preliminary pressurizations can be regulated by the pressure regulator (not shown), and the common constant preliminary pressure (discharge pressure) of fuel is held constant like this.The transfer the fuel of discharging from transfer pump 72 is supplied to pressurized chamber 95 through 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 through the chokes portion of not describing (being also referred to as restriction, throttled portion).
The pumping configuration of high-pressure service pump 10 comprises cam 83, piston 13 and the cam ring 84 of live axle 80.Cam ring 84 is placed between cam 83 and the piston 13 and the driving force of live axle 80 is directed at piston 13.The pumping configuration is further pressurizeed to the transfer the fuel of discharging from transfer pump 72 in pressurized chamber 95, and pumping configuration pumping is by the fuel of further pressurization.
Piston 13 is set at along the direction perpendicular to central shaft 80j and eccentric shaft 83j on the side of cam 83 of live axle 80.
The 13a of push rod portion is formed at the end place of cam 83 sides of piston 13, make the 13a of push rod portion relatively slidably contacting part 85 slidably, slidably contacting part 85 is formed in the outer wall of cam ring 84 along the L-R direction of Fig. 1.Especially, the end of the 13a of push rod portion 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 push rod portion 13a end of piston 13.
Cam ring 84 is constructed to polygonal, makes cam ring 84 comprise said plat surface (corresponding to contacting part 85 slidably) and arcuate surfaces.The inwall of cam ring 84 is constructed to circle (cylindrical shape).The 3rd bearing housing 88 is fixed in the inwall of cam ring 84.It is rotatable that the 3rd bearing housing 88 is constructed to the cam 83 of circle (cylindrical shape) relatively.
Piston spring 19 is maintained between the 13a of push rod portion and valve chest 12 of piston 13, makes piston spring 19 extending axially along pipe portion 18.By this, the 13a of push rod portion of piston 13 withstands on the slidably contacting part 85 of cam ring 84 all the time.
The rotation of cam ring 84 receives the restriction that is applied to the fuel pressure on the piston 13 in thrust and the pressurized chamber 95 of piston spring 19.Cam ring 84 self does not rotate.But cam ring 84 moves back and forth along the L-R direction among Fig. 1 around the central shaft 80j of live axle 80 rotation and in response to cam 83 motions due to live axle 80 rotations.
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, for purpose of description, piston along among Fig. 1 to the right moving of direction will be called as moving upward of piston 13, and piston along among Fig. 1 left moving of direction be called as moving downward of piston 13.
When piston 13 moves downward (motion towards the left side among Fig. 1), transfer the fuel is pumped down in the pressurized chamber 95 from inlet channel 91 through said entering control valve unit 30A.On the contrary, when piston 13 moves upward (motion towards the right side among 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 set in the fuel channel 96, and fuel 95 is discharged from from the pressurized chamber through fuel channel 96.One-way valve 68 has limited from the pressurized chamber the 96 discharge fuel towards rail and Fuelinjection nozzle discharge altogether and has been back in the pressurized chamber 95.When the internal pressure of pressurized chamber 95 was opened pressure above the valve of one-way valve 68, common rail and Fuelinjection nozzle are exported and be conducted to pressurized fuel under high pressure through outlet passage 97 from exporting 98.
Next, will entering control valve unit 30A and solenoid actuator 50A be described with reference to Fig. 2-4B.
Get into valve 30A and comprise base member 31, valve element 32, first spring (as first push mechanism or the first promotion instrument) 33, holding member 34 and plug screw 39.Get into control valve unit 30A and open or close the fuel channel that extends to pressurized chamber 95 from inlet channel 91.
Base member 31 is constructed to tubular shape roughly and is placed in the at of the valve receiving opening 16 of valve chest 12.Base member 31 comprises axis hole 311 and a plurality of intercommunicating pores 313.Axis hole 311 is shaped as along the extension of central axis of base member 31.Each intercommunicating pore 313 radially is 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 chamber (fuel well chamber) 93.
The surface of axially going up the solenoid actuator 50A side of a solenoid actuator 50A side of living in that is placed in of base member 31 is constructed to stepped shaft.The end face that is positioned at radially inner side 314 of base member 31 forms the spring pedestal of first spring 33.In addition, plug screw 39 so is installed on valve chest 12 so that the external screw thread that is configured as plug screw 39 periphery walls screws togather with the female thread that is configured as valve receiving opening 16 inner circle walls.When the stepped surfaces that is positioned at radial outside 315 of base 31 is promoted by plug screw 39, base member 31 be pushed against with the bottom of being fixed in valve receiving opening 16.
In the surface of the pressurized chamber of base member 31 95 sides, form taper concave surface pedestal part 316 around axis hole 311.But valve portion 321 seatings that in the distal portion of valve element 32, form are on pedestal part 316.
Valve element 32 is constructed to a shape (rod), and comprises valve portion 321, mid diameter portion 322 and minor diameter 323, and 95 sides begin positioned adjacent from the pressurized chamber vertically for they.Valve portion 321 has maximum outside diameter and is tapered to form tapered portion with the pedestal part 316 corresponding to base member 31 on opposite with the pressurized chamber 95 in the axial direction side in valve element 32.
Mid diameter portion 322 is received in the axis hole 311 of base member 31 slidably.In the peripheral part section of the periphery wall of mid diameter portion 322, form par 325 between the inner circle wall of par 325 and axis hole 311, fuel channel to be provided.
Form neck (limitation part) 324 between valve portion 321 in valve element 32 and the mid diameter portion 322, neck 324 extends from the tapered portion of valve portion 321 continuously.Neck 324 forms in the position corresponding to the axis hole 311 of base member 31, makes between the inner circle wall of neck 324 and axis hole 311, to form annular pass 92.
Holding member 34 for example is assemblied in the minor diameter 323 of valve element 32 through press fit on the solenoid actuator 50A of base member 31 side.Stretch out from the end radially outward that is positioned at solenoid actuator 50A one side of the periphery wall of holding member 34 and to form flange 341.First spring 33 is sandwiched between the end face 314 of flange 341 and base member 31 of holding member 34.In the peripheral part of holding member 34, form groove 342 so that fuel channel to be provided.
When holding member 34 was fixed in valve element 32, the axial movable scope of valve element 32 and holding member 34 was restricted.In addition, when valve element 32 not being applied external force, valve element 32 along the valve closing direction promoted by the thrust of first spring 33 so that valve portion 321 seatings on pedestal part 316.
Solenoid actuator 50A comprises coil 51, first stator 52, mobile core 53, second stator 54, flange (the 3rd stator) 55A, bar 41, second spring (as second push mechanism or the second promotion instrument) 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.
Form coil 51 through twining lead around the spool that is formed from a resin 58.When coil 51 energisings, form magnetic attraction at flange (the 3rd stator) 55A place, and this magnetic attraction is applied between flange 55A and the mobile core 53.Therefore, mobile core 53 moves along direction left in Fig. 2-4B.After this be purpose of description, the direction left among Fig. 2-4B will be called as the suction direction, and the direction to the right among Fig. 2-4B will be called as the back suction force direction.
First stator 52, second stator 54 and flange (the 3rd stator) 55A are processed by magnetic material.The axial positions of first stator 52 on opposite with the pressurized chamber 95 vertically side of flange 55A places the radially inner side of coil 51.Second stator 54 is connected between the flange 55A and first stator 52 with being placed as the peripheral part that covers coil 51 and magnetic force.
Be installed in opposite with the pressurized chamber 95 in the axial direction end of valve chest 12 as the flange 55A of the 3rd stator.Opposite with the pressurized chamber 95 in the axial direction suction face 551A of flange 55A is relative with mobile core 53.In flange 55A, form axis hole 552 and admit chamber 553 with spring.Axis hole 552 is admitted bar 41.Spring admits chamber 553 in suction face 551A, to center on axis hole 552 openings.
Here, the external diameter of supposing the suction face 551A of flange 55A is φ d1, and the diameter of the chamfering opening portion section of spring admittance chamber 553 is φ d2.In this case, magnetic cross-sectional area SA, promptly the surface area of suction face 551A is expressed through following equation (1).
SA=π/4 * (φ d1-φ d2) 2Equation (1)
The pad of being processed by nonmagnetic substance 59 is placed between first stator 52 and the flange 55A.Pad 59 for example is incorporated into first stator 52 and flange 55A through welding or soldering.Thereby pad 59 has been blocked magnetic flux and has been suppressed the magnet short-cut path between first stator 52 and the flange 55A.
Mobile core 53 is processed and is constructed to the pipe body by magnetic material.Mobile core 53 axially is placed between first stator 52 and the flange 55A and radially is placed on the inboard of first stator 52 and pad 59.Mobile core 53 is suitable for to-and-fro motion vertically.When coil 51 energising, mobile core 53 attracts and therefore moves towards flange towards the flange 55A as the 3rd stator.In addition, mobile core 53 has and extends axially the intercommunicating pore 531 that passes mobile core 53.By this, reciprocating the time, the pressure on pressure on mobile core 53 front sides and mobile core 53 rear sides roughly keeps constant through intercommunicating pore 531.
Bar 41 and mobile core be 53 integrally formed, more particularly for example through welding, soldering or riveted fixing in mobile core 53, thereby form and mobile core 53 synergistic armature assemblies (removable configuration) 40A.Bar 41 passes the axis hole 552 quilt admittances of flange 55A and is suitable for vertically with mobile core 53 to-and-fro motion.Bar 41 to be positioned at the end of end and valve element 32 on pressurized chamber's 95 1 sides along the suction direction relative.After this, for purpose of description, armature assembly 40A will be called as along moving of suction direction and travel forward, and armature assembly 40A will be called as backward along moving of back suction force direction and move.
The second spring 43A is accepted in the spring of flange 55A and admits in the chamber 553.The end in contact spring of the second spring 43A is admitted the bottom surface of chamber 553, and the other end of the second spring 43A contacts the end face on the flange 55A side of living in that is positioned at of said mobile core 53.The second spring 43A promotes mobile core 53 and bar 41 along the back suction force direction.At this moment, the end of bar 41 contacts the stop member 57 in the inner bottom part that is placed on first stator 53, thereby has limited the motion backward of bar 41.
Next, with the operation of describing high-pressure service pump 10.In high-pressure service pump 10, piston 13 is along with the rotation of the cam 83 of live axle 80 is synchronously moved along the L-R direction of Fig. 1 up or down, the circulation of repeated admission stroke, metering stroke (metering stroke) and compression stroke.
(initial conditions)
When coil 51 was not energized, mobile core 53 was promoted (referring to Fig. 2) by the thrust of the second spring 43A towards stop member 57, made bar 41 contactor banking stop spares 57.At this moment, valve element 32 is by the thrust seating of first spring 33 (referring to Fig. 2 and 4A) on pedestal part 316.
Thereby fuel can pass the fuel channel of the groove 342 of the par 325 that is defined to mid diameter portion 322 and fuel channel between axis hole 311 inner circle walls and holding member 34 to flow between annular pass 92 and fuel bath chamber 93, so that the fuel pressure of the fuel pressure of annular pass 92 and fuel bath chamber 93 is roughly mutually the same.
(aspirating stroke)
When the lift of cam 83 began to reduce in aspirating stroke, piston 13 moved downward.By this, thus pressurized chamber 95 is depressurized between annular pass 92 and pressurized chamber 95 and produces pressure reduction.When the fuel pressure of annular pass 92 increased the thrust that surpasses first spring 33, valve element 32 began to leave, and the valve that promptly lifts away from pedestal part 316 and therefore started valve element 32 is opened.
When coil 51 energisings, the electromagnetic attraction that is directly proportional with magnetic circuit cross-section area SA is applied between flange 55A and the mobile core 53.When magnetic attraction increased the thrust that surpasses the second spring 43A, armature assembly 40A (bar 41 and mobile core 53) began to travel forward, and promptly rises along the suction direction.Subsequently, the far-end of bar 41 contacts valve element 32 and opens direction along valve and promotes valve element 32.During the energising of coil 51 (current"on"time), bar 41 remains on valve open mode (referring to Fig. 3 and 4B) with valve element 32.
Under the valve open mode, fuel passes annular energising 92 inflow pressurized chambers 95 (referring to the solid arrow F1 Fig. 4 B) from inlet channel 91.Part fuel can pass the fuel channel mobile (shown in dotted arrow F among Fig. 4 B 2) between annular pass 92 and fuel bath chamber 93 of the groove 342 of fuel channel and holding member 34 between the inner circle wall of the par 325 that is defined to mid diameter portion 322 and axis hole 311.By this, the fuel pressure of the fuel pressure of annular pass 92 and fuel bath chamber 93 becomes roughly mutually the same, and what flow between annular pass 92 and the fuel bath chamber 93 the slide part between fuel lubricated valve element 32 and the base member 31.
(metering stroke)
When the motion of cam 83 at lower dead centre (bottom dead center) thus locating to become moves upward when moving up piston 13, operation becomes the metering stroke from aspirating stroke.At this moment, keep the energising of coil 51, and valve element 32 is maintained at the valve open mode.In response to moving upward of piston 13, thereby the fuel that is drawn into pressurized chamber 95 is flow back to annular pass 92 metering fuels.
(compression stroke)
When breaking off the energising of coil 51, the electromagnetic attraction between mobile core 53 and the flange 55A has just lost.Subsequently, armature assembly 40A moves along the 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 the valve closing direction by the thrust of first spring 33.
Therefore, fuel 95 92 the discharges that just are through with from the pressurized chamber to the annular pass.Subsequently, thus when the interior pressure in response to the pressurized chamber 95 that moves upward of piston 13 increased the valve that exceeds one-way valve 68 and opens pressure, fuel passed outlet passage 97 and discharges (referring to Fig. 1) from exporting 98.
Here, the load on spring of the load on spring of first spring 33 and the second spring 43A is so set so that the valve closing velocity (movement velocity) of armature assembly 40A valve element 32 when the movement velocity of back suction force direction is higher than the energising of breaking off coil 51.Especially, the thrust of the second spring 43A is set to the thrust greater than first spring 33.
Like this, in case lost electromagnetic attraction, armature assembly 40A just moves along the back suction force direction backward, and valve element 32 moves along the valve closing direction subsequently.Especially, armature assembly 40A and valve element 32 move by thrust independently independently of one another.
Next, will compare the advantage of describing the embodiment of the invention with a comparative example.
Fig. 8 illustrates the solenoid valve of a comparative example, and it is used as the entering control valve unit 20C of high-pressure service pump.Get into control valve unit 20C and have valve member 21, it is placed in the space between valve outer body 23 and the interior body 24 of valve.Valve member 21 is accepted in the spring of body 24 in the valve and admits first spring 22 in the chamber 242 to promote, and makes valve member 21 seatings on the pedestal part 231 of valve outer body 23.
In solenoid actuator 50C, second spring 56 is placed between end and the stop member 57 of needle 61 and along the suction direction and promotes needle 61 (direction left among Fig. 8).The thrust of second spring 56 is set to the thrust less than first spring 22.Therefore, under the off-position of coil 51, valve member 21 seatings are on pedestal part 231 and do not receive the influence of the thrust of second spring 56.
Fig. 2 with 3 in the assembly of the solenoid actuator 50C shown in the same reference numerals basically with first embodiment's solenoid actuator 50A in identical.
Though the position of the vibration-direction of piston 13 and inlet channel 911 all with first embodiment in different, these differences are not substantial difference.
When coil 51 energisings, electromagnetic attraction puts between flange 55C and the mobile core 53.Then, needle 61 by the thrust of the electromagnetic attraction and second spring 56 along suction direction travel forward (direction left among Fig. 8).
Be used under the situation in the high-pressure service pump getting into control valve unit 20C, valve member 21 is opened by the pressure reduction between the pressure on pressure on valve member 21 upstream sides and valve member 21 downstream sides, in first embodiment.In addition, even between the upstream side of valve member 21 and downstream side, do not produce pressure reduction, when proal needle 61 impelled the thrust of valve member 21 opposings first spring 22, valve member 21 was opened under the thrust of first spring 22.Therefore, inlet channel 911 communicates with each other through the passage in body 24 inboards in valve outer body 23 and the valve with pressurized chamber 95.
20C is used under the situation of high-pressure service pump at the entering control valve unit, and the flange 611 that is arranged at needle 61 helps to open through upstream side that uses flange 611 and the valve that the pressure reduction between the downstream side carries out valve member 21.
When breaking off the energising of coil 51, the electromagnetic attraction that puts on mobile core 53 has disappeared.Under the power difference effect between the thrust of the thrust of first spring 22 and second spring 56, valve member 21 moves along the valve closing direction, like this valve member 21 impel needle 61 along the back suction force direction move (direction to the right among Fig. 8) and seating on pedestal part 231.Therefore, valve member 21 need carry out extra work (promptly having the extra work amount): the thrust of when valve cuts out, except that its required valve closing movement, impelling needle 61 opposings second spring 56.The influence of this operation of valve member 21 will be described with reference to Fig. 9 A-9E.
Fig. 9 A-9E illustrates the operating characteristics of the solenoid valve of the entering valve that is used as high-pressure service pump.Especially, Fig. 9 A is the time dependent chart of lift that cam is shown.Fig. 9 B is that time dependent chart is ordered in the energising (open, close) that coil is shown.Fig. 9 C is illustrated in the moving time dependent chart of electric current of coil midstream.Fig. 9 D is the lift lift (in Fig. 9 D shown in solid line) over time of (among Fig. 9 D shown in dotted line) and needle 61 over time that valve member 21 is shown.Fig. 9 E is the time dependent chart of pump output that fuel is shown.
At time point ta, the lift variation of cam is that cam begins to move downward to accomplish aspirating stroke from upper dead center (TDC).At this moment, the fuel pressure of pressurized chamber 95 reduces, and owing to the pressure reduction between the pressure on pressurized chamber's one side of pressure on upstream passageway 912 1 sides of valve member 21 and valve member 21, valve member 21 is opened direction along its valve and moved like this, and valve is opened at moment t2 and accomplished.In addition, at time point t1, open the energising of order (energization ON command) opening coil 51 and generation electromagnetic attraction at solenoid actuator 50C place by energising.Subsequently, needle 61 travels forward and arrives the proal limit (full lift) at time point t3.
Lift at time point tb cam arrives lower dead centre (BDC), and aspirating stroke converts the metering stroke into by this.Arrive peaked electric current at time point t4 and be energized ON-and OFF-command (energization OFF command) at time point tc and stop, this is based on, and required fuel-pumping amount confirms.Subsequently, valve member 21 promotes needle 61 and closes along moving direction backward.When the load backward of promotion needle 61 increased, valve response closing period TvC (that is the time point t5 that, closes to the valve of accomplishing valve member 21 from the time point tc that breaks off energising) was elongated.Here, the elongated deterioration that also is referred to as the valve response closing of valve response closing period.
After the time point tc that breaks off energising, operation is shown as from the metering stroke and becomes compression stroke.But the fuel of pressurized chamber 95 does not turn back to upstream passageway 912 during valve response closing period TvC.Therefore in fact do not accomplish the pressurization and the discharge (pumping) of fuel.
Subsequently, begin to carry out the discharge and the pressurization of fuel from time point t5, this is after valve response closing period TvC goes over.But this moment, the position of cam arrived upper dead center, and remaining up stroke is very little.Therefore, the pump output QC of fuel has reduced.Therefore, the deterioration of valve response closing causes the minimizing of fuel-pumping amount, promptly with respect to required fuel duty, and the shortage of fuel-pumping amount.
As stated, be applied to need high-speed response under the situation of equipment, so the valve response closing of solenoid valve becomes problem is arranged very much at the solenoid valve of this comparative example.Next, the operating characteristics of this comparative example will with the operating characteristics contrast with reference to first embodiment of Fig. 5 A-5E.
The parameter of Fig. 5 A-5E is identical with Fig. 9 A-9E's.But be noted that different with Fig. 9 D to be that the lift that Fig. 5 D illustrates valve element 32 (dots among Fig. 5 D) over time and the lift of armature assembly 40A (is represented with solid line among Fig. 5 D) over time.In addition, roughly the same from aspirating stroke to the working state of measuring stroke and this comparative example.Especially, the relative electromagnetic attraction loss of the thrust of the second spring 43A when opening the energising of coil 51, so time point t3 trends towards postponing.But this function to high-pressure service pump does not have materially affect.
After time point tc broke off the energising of coil 51 with the 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 (direction to the right among Fig. 1), armature assembly 40A moved along the back suction force direction backward.Then, by the thrust of first spring 33 and need not drive armature assembly 40A as its load, valve element 32 only moves along the valve closing direction.Therefore, the quick valve closing movement of valve element 32 is possible.Therefore, valve response closing period TvA---the time point t5 from the time point tc of the valve closing movement of open valve element 32 to the valve closing movement of accomplishing valve element 32---can be shortened, and therefore improve the valve response closing.
Like this, still have capacity up stroke, therefore increased the pump output QA of fuel to cam top dead.Therefore, the valve response closing can be improved, and the fuel-pumping amount of the required supply of relative fuel can be suitably reached.
Fig. 6 is the chart of valve response closing of entering control valve unit 20C of valve response closing and this comparative example that first embodiment's entering control valve unit 30A is shown.
As shown in Figure 6, when the load on spring of first spring 22 of the load on spring of first embodiment's first spring 33 and comparative example increased, the valve response closing period had been shortened.For example; It is all identical to suppose that other factors (like the weight and the move distance of removable configuration) except that first spring is set in first embodiment and comparing embodiment, and the load on spring of first spring also is identical in first embodiment and comparing embodiment.Like this, compare with the entering control valve unit 20C of comparative example, first embodiment's entering control valve unit 30A can shorten the valve response closing period.
(second embodiment)
Next, second embodiment of the disclosure of invention will be described with reference to Fig. 7.The parts identical with first embodiment are represented with identical reference character, repeat no more.
Similar with first embodiment, second embodiment's solenoid valve is used as the entering control valve unit 30B of high-pressure service pump.The difference that gets into the control valve unit 30B and first embodiment's entering control valve unit 30A is the shape of bar, the shape of flange and the position of second spring.
Bar 42 has flange 421, and its a part of radially outward that is positioned at base member 31 sides from flange (as stator core) 55B stretches out.Be placed in the radially outer of first spring 33 as the second spring 43B of second push mechanism or the second promotion instrument.The end in contact flange 421 of the second spring 43B, and the end face 314 of the other end of 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 (direction to the right among Fig. 7).
In addition, different with first embodiment's flange 55A, flange 55B need not admit chamber 553 at the spring that the suction face of flange 55B is opened.
Here, the external diameter of supposing the suction face 551B of flange 55B is φ d3, and the diameter of the chamfering opening portion section of axis hole 552 is φ d4.Like this, magnetic cross-sectional area SB, promptly the surface area of suction face 551B can be represented by following equation (2).
SA=π/4 * (φ d1-φ d2) 2Equation (2)
When coil 51 energisings, the electromagnetic attraction that is directly proportional with magnetic circuit cross-section area SB is applied between flange 55B and the mobile core 53.Armature assembly 40B travels forward along the thrust of suction direction (direction left among Fig. 7) the antagonism second spring 43B, and bar 42 promotes valve element 32.Subsequently, the thrust of valve element 32 antagonism first spring 33 is moved and is opened.
When breaking off the energising of coil 51, armature assembly 40B moves along the thrust of back suction force direction (direction to the right among Fig. 7) the antagonism second spring 43B backward.In addition, valve element 32 by the thrust of first spring 33 along the valve closing direction move and seating on pedestal part 316.At this moment; The load on spring of the load on spring of first spring 33 and the second spring 43B is so set so that the movement velocity of armature assembly 40B is higher than the valve closing velocity (movement velocity) of valve element 32, i.e. the motion of armature assembly 40B is prior to the valve closing movement of valve element 32.Like this, be similar to first embodiment, possibly improve the valve response closing of valve element 32.
In addition, in a second embodiment, magnetic circuit cross-section area SB is limited aforesaid equation (2).Therefore, for producing the electromagnetic attraction identical with first embodiment, magnetic circuit cross-section area SB can be set equal to first embodiment's magnetic circuit cross-section area SA (referring to equation (1)).Therefore, the diameter phi d4 of the chamfering opening portion section of second embodiment's axis hole 552 is less than first embodiment's diameter phi d2, because lack the cause that spring is admitted chamber 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 further improve the valve response closing that gets into control valve unit 30B.
Improvement to the foregoing description will be described now.
(A) in the above-described embodiments, the load on spring of the load on spring of first spring 33 and the second spring 43A, 43B so set so that when breaking off the energising of coil 51 armature assembly 40A, 40B be higher than the valve closing velocity (movement velocity) of valve element 32 along the movement velocity of back suction force direction.But the movement velocity of armature assembly 40A, 40B not necessarily is higher than the valve closing velocity of valve element 32.
When the movement velocity of armature assembly 40A, 40B was lower than the valve closing velocity of valve element 32 of the ideal case that lacks armature assembly 40A, 40B, the valve closing velocity of valve element 32 received the restriction of the movement velocity of assembly 40A, 40B.
Even but in this case, armature assembly 40A, 40B are pushed and move with valve element 32 identical directions in the edge.Therefore, only diminished with respect to the speed difference of the valve closing movement of valve element 32.Especially, compare with the comparative example (wherein the needle 61 edges direction opposite with the valve closing direction of valve element 32 is pushed) of Fig. 8, the valve closing movement of valve element 32 obviously is preferred.Therefore, even in this case, also can realize the advantage of the disclosure of invention.
(B) in second embodiment's entering control valve unit 30B, the flange 421 opposite ends second spring 43B and bar 42 contact the end face 314 of base member 31.The disclosure of invention is not limited thereto.That is to say that the flange 421 opposite ends second spring 43B and bar 42 can be fixed in any suitable member.For example, in the inwall of plug screw, can form end difference, and the end of the second spring 43B can contact this end difference.
(C) in the above-described embodiments, one group of piston 13, entering control valve unit 30A, 30B and solenoid actuator 50A, 50B are arranged in the high-pressure service pump 10.But the disclosure of invention is not limited thereto.Many cover (group) pistons, entering control valve unit, solenoid actuator can center on the live axle setting in high-pressure service pump.
(D) solenoid actuator of the disclosure of invention is not limited to be applied to the high-pressure service pump of DENG.For example, the solenoid valve of the disclosure of invention can be applicable to the entering control valve unit of petrolic high-pressure service pump.In addition, the solenoid valve of the disclosure of invention can be applicable to any other suitable equipment as needing the Fuelinjection nozzle of high-speed response.
As stated, the disclosure of invention is not limited to the foregoing description and improvement thereof.That is to say that the foregoing description and improve can be modified in many ways and not break away from the spirit and scope of the present invention.

Claims (5)

1. solenoid valve comprises:
Be suitable for reciprocating valve element (32);
The base member (31) that comprises pedestal part (316), wherein said valve element (32) are gone up and can be opened direction along valve in said pedestal part (316) along valve closing direction ability seating and lift away from said pedestal part (316);
First push mechanism (33), it is pushed against said valve element (32) on the said pedestal part (316) along said valve closing direction;
Comprise and twine coil of conductive wire (51);
Stator core (55A, 55B), it produces magnetic attraction when said coil (51) is switched on;
Mobile core (53), it is suitable for putting on said stator core at magnetic attraction, and (55A moves along the suction direction in the time of 55B) and between the said mobile core (53);
Be fixed in said mobile core (53) thus with the bar (41 of mobile core (53) one motion; 42); Wherein work as in response to the said bar (41 of the energising of coil (51); 42) with said mobile core (53) when suction direction one is moved, an end of said bar (41,42) the said valve element of contact (32) and open direction along said valve and promote said valve element (32); And
Second push mechanism (43A, 43B), its edge promotes said mobile core (53) and said bar (41,42) with suction back suction force direction in the opposite direction, wherein:
Said valve closing direction is identical with said back suction force direction; Said valve closing direction is the pushing direction that is used to promote first push mechanism (33) of said valve element (32); Said back suction force direction is to be used to promote said mobile core (53) and bar (41; 42) second push mechanism (43A, pushing direction 43B); And
When breaking off the energising of coil (51); Said mobile core (53) and bar (41; 42) by the second push mechanism (43A; Thrust 43B) is moved along said back suction force direction, and said valve element (32) moves along said valve closing direction by the thrust of first push mechanism (33) simultaneously.
2. according to the solenoid valve of claim 1; Wherein, When breaking off the energising of coil (51), said mobile core (53) and bar (41,42) are suitable for to move along the back suction force direction along the high movement velocity of the movement velocity of valve closing direction than said valve element (32).
3. according to the solenoid valve of claim 1; One end in contact stator core (55A) of wherein said second push mechanism (43A); And, second push mechanism (43A) contact said mobile core (53) with the opposite the other end of a said end second push mechanism (43A).
4. according to the solenoid valve of claim 1; The flange (421) of the said bar of one end in contact (42) of wherein said second push mechanism (43B), and second push mechanism (43B) be fixed with the opposite the other end of a said end second push mechanism (43B).
5. high-pressure service pump comprises:
Piston (13);
Admit the cylinder (14) of said piston (13), wherein piston (13) is suitable for to-and-fro motion in cylinder (14);
Housing (12) comprising:
Pressurized chamber (95), wherein fuel is pressurizeed by piston (13); And
Supply fuel to the inlet channel (91) of said pressurized chamber (95); And
Entering control valve unit (the 30A that comprises the solenoid valve that claim 1-4 is any; 30B); Wherein said entering control valve unit (30A; 30B) be suitable for to-and-fro motion in response to piston (13) and be opened or close, so that be communicated with or be not communicated with between said inlet channel (91) and said pressurized chamber (95).
CN201210194071.0A 2011-06-13 2012-06-13 Solenoid valve and high-pressure pump having same Active CN102828874B (en)

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CN107401466A (en) * 2017-08-18 2017-11-28 成都威特电喷有限责任公司 High oil absorption power diesel engine single body pump
CN113700929A (en) * 2021-08-29 2021-11-26 中国船舶重工集团公司第七一九研究所 Pilot-operated high-pressure air electromagnetic valve

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