EP0834013B1 - Brennstoffpumpe - Google Patents

Brennstoffpumpe Download PDF

Info

Publication number
EP0834013B1
EP0834013B1 EP96914714A EP96914714A EP0834013B1 EP 0834013 B1 EP0834013 B1 EP 0834013B1 EP 96914714 A EP96914714 A EP 96914714A EP 96914714 A EP96914714 A EP 96914714A EP 0834013 B1 EP0834013 B1 EP 0834013B1
Authority
EP
European Patent Office
Prior art keywords
control valve
valve body
piston
piston valve
interval
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP96914714A
Other languages
English (en)
French (fr)
Other versions
EP0834013A4 (de
EP0834013A1 (de
Inventor
Robert D. Straub
Werner Faupel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Diesel Technology Co
Original Assignee
Diesel Technology Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Diesel Technology Co filed Critical Diesel Technology Co
Publication of EP0834013A1 publication Critical patent/EP0834013A1/de
Publication of EP0834013A4 publication Critical patent/EP0834013A4/de
Application granted granted Critical
Publication of EP0834013B1 publication Critical patent/EP0834013B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/306—Fuel-injection apparatus having mechanical parts, the movement of which is damped using mechanical means

Definitions

  • the present invention relates to a fuel pump control valve assembly and method of operating same for dampening control valve motion in a heavy duty truck diesel fuel injection system including either a unit pump or unit fuel injectors.
  • Fuel control valve assemblies in vehicular fuel injection systems typically include a housing having a control valve chamber, a control valve having a piston valve body, and a valve stop. Electromagnetic actuators are commonly used in control valve assemblies for electronically controlling actuation of the control valve. Examples are shown in U.S. Patent Numbers 4,618,095, assigned to the assignee of the present invention, and 4,501,246.
  • a primary disadvantage associated with existing control valve assemblies is the fact that upon contact of the control valve with the control valve stop, the control valve may "bounce” off the valve stop in diminishing series fashion as illustrated in Figure 6a before finally closing. This control valve "bounce” can significantly lessen the precision of the fuel flow process, and thereby the combustion efficiency.
  • the present invention also contemplates such a control valve assembly wherein the damping of the control valve at one or both ends of its stroke may be controlled electronically by adjusting current levels to the control valve armature coil and the one of this control technique particularly in pilot injection type fuel injection systems thereby facilitating precise control over the initiation of the pilot injection by the precise control of the end of the preceding main injection illustrated as t2 in Figures 6b and 6c.
  • the control valve assembly comprises a housing having a control valve disposed in a control valve chamber.
  • the control valve includes a piston valve body axially movable over a motion displacement interval between first and second positions within the control valve chamber.
  • the motion displacement interval is defined by first and second sub-intervals that are each bounded on one end by the first and second positions, respectively.
  • the piston valve body includes a piston valve body seat. The piston valve body seat contacts a pump body seating surface whenever the piston valve body is in the first position.
  • a valve stop is disposed in the housing adjacent the control valve chamber.
  • the piston valve body seat contacts the valve stop whenever the piston valve body is in the second position.
  • a first control valve spring resiliently biases the piston valve body toward the second position whenever the piston valve body is in the first sub-interval.
  • a second control valve spring resiliently biases the piston valve body into damped engagement with the valve stop whenever the piston valve body is in the second sub-interval.
  • control valve assembly includes means for actuating the control valve, such as an electromagnetic actuator or solenoid.
  • the piston valve body is urged toward an actuated position whenever the control valve is in an actuated state.
  • the actuated position can be either the first or second position, and an unactuated position is the other of the first and second positions.
  • the first control valve spring resiliently biases the piston valve body toward the unactuated position whenever the piston valve body is in the first sub-interval.
  • the second control valve spring resiliently biases the piston valve body into damped engagement with the valve stop whenever the piston valve body is in the second sub-interval.
  • first and second control valve springs in accordance with the present invention.
  • first control valve spring could alternatively be configured to resiliently bias the piston valve body toward the second position when the piston valve body is in the second sub-interval, in addition to whenever the piston valve body is in the first sub-interval.
  • the second control valve spring could be configured to resiliently bias the piston valve body toward the first position when the piston valve body is in the second sub-interval, or alternatively, the second control valve spring could be configured to resiliently bias the piston valve body toward the second position when the piston valve body is in the second sub-interval.
  • the direction which the second control valve spring biases the piston valve body, for a particular configuration is determined accordingly so as to bring the piston valve body into damped engagement with the valve stop.
  • the second control valve spring resiliently biases the piston valve body into damped engagement with the valve stop when the piston valve body is in the first sub-interval, in addition to whenever the piston valve body is in the second sub-interval.
  • the control valve assembly of the present invention has many useful applications.
  • One such application is to use the control valve assembly in a fuel pump or fuel injector for a fuel injection system for an internal combustion engine.
  • a pump constructed according to the present invention, comprises a pump body having a pumping chamber, a fuel inlet for supplying fuel to the pumping chamber, an output port, and a control valve chamber between the pumping chamber and the outlet port.
  • a reciprocating plunger is disposed in the pumping chamber. The plunger is reciprocatable over a stroke range between an extended position and a retracted position. A plunger spring resiliently biases the plunger to the retracted position.
  • the pump further comprises an actuatable control valve for controlling fuel.
  • the control valve is disposed in the control valve chamber, and the control valve includes a piston valve body axially movable over a motion displacement interval between first and second positions within the control valve chamber.
  • the motion displacement interval is defined by first and second sub-intervals bounded by the first and second positions, respectively.
  • the piston valve body includes a piston valve body seat. The piston valve body seat contacts a pump body seating surface whenever the piston valve body is in the first position.
  • the pump further comprises a stator assembly, and means for actuating the control valve, such as an electromagnetic actuator or solenoid, disposed in the stator assembly.
  • the piston valve body is urged toward an actuated position whenever the control valve is in an actuated state.
  • An armature is secured to the control valve, and a valve stop is disposed in the pump body adjacent the control valve chamber.
  • the piston valve body seat contacts the valve stop whenever the piston valve body is in the second position.
  • a first control valve spring resiliently biases the piston valve body toward the unactuated position whenever the piston valve body is in the first sub-interval.
  • a second control valve spring resiliently biases the piston valve body into damped engagement with the valve stop whenever the piston valve body is in the second sub-interval.
  • a stop plate secures the valve stop within the pump body.
  • a stator spacer is disposed between the pump body and the stator assembly and has a central opening for receiving the armature therein.
  • a plurality of fasteners mount the stator assembly and the stator spacer on the pump body.
  • a piston is received in the piston valve body.
  • the piston has first and second ends, and a periphery surface. The first end abuts the valve stop; the second end abuts an end of the second control valve spring.
  • the second control valve spring is received in the piston valve body.
  • the piston has a flow passage in the form of a slot, or plurality radially and/or axially sequenced ports, for accommodating fluid flow formed on the periphery surface of the piston.
  • the flow passage extends from the second end toward the first end.
  • the flow passage extends outboard of the piston valve body whenever the piston valve body is in the first sub-interval.
  • the flow passage is enclosed by the piston valve body whenever the piston valve body is in the second sub-interval.
  • a method for controlling rate of displacement of the control valve is provided.
  • the electric current can be precisely controlled to cause the piston valve body movement to model the piston valve body movement for the previously described control valve assemblies.
  • control valve assembly or method of the present invention can be used in pumps or injectors having either a vertical or horizontal orientated plunger.
  • a pump 10 including a first embodiment of a control valve assembly made in accordance with the present invention is illustrated.
  • the pump 10 has a pump body 12, and a pumping chamber 14 is enclosed by pump body 12.
  • a fuel inlet 16 for supplying fuel to pump 10 is located on the periphery of pump body 12.
  • Pump body 12 further has an outlet port 18, and a control valve chamber 20 between pumping chamber 14 and outlet port 18.
  • Passageways 22 and 24 connect pumping chamber 14, control valve chamber 20, and outlet port 18, respectively.
  • a reciprocating plunger 26 is disposed in pumping chamber 14. Plunger 26 is reciprocatable over a stroke range between an extended position indicated at A and a retracted position indicated at B. A plunger spring 28 resiliently biases plunger 26 to the retracted position B.
  • a stator assembly 30 contains an electromagnetic actuator 32, such as a solenoid.
  • An electromagnetically actuated control valve 34 is disposed in control valve chamber 20 for controlling fuel.
  • Control valve 34 includes a piston valve body 36. Piston valve body 36 is movable between an unactuated position and an actuated position within control valve chamber 20.
  • Control valve chamber 20 contains passageways 38 for fuel flow.
  • An armature 40 is secured to control valve 34 by a fastener such as a screw 42.
  • a valve stop 44 is disposed in pump body 12 adjacent to control valve chamber 20.
  • An O-ring 46 encircles valve stop 44 to prevent fuel leakage.
  • a stop plate 48 secures valve stop 44 within pump body 12.
  • a stator spacer 50 having a central opening 52 for receiving armature 40 therein is disposed between pump body 12 and stator assembly 30.
  • Stator spacer 50 has notches 54 for receiving a retainer 56.
  • O-rings 58 seal stator spacer 50 against stator assembly 30 and pump body 12.
  • Fasteners 60 mount stator assembly 30 and stator spacer 50 on pump body 12.
  • Piston valve body 36 is axially movable over a motion displacement interval between first and second positions within control valve chamber 20.
  • the actuated position of piston valve body 36 is one of the first and second positions, and the unactuated position is the other of the first and second positions.
  • Piston valve body 36 is urged toward the actuated position whenever control valve 34 is in the actuated state.
  • the motion displacement interval for piston valve body 36 is defined by first and second sub-intervals defined by the first and second positions for piston valve body 36, respectively.
  • a first control valve spring 70 resiliently biases piston valve body 36 toward the unactuated position whenever piston valve body 36 is in the first sub-interval.
  • a spring seat 72 and retainer 56 abut first and second ends of first control valve spring 70.
  • a second control valve spring 76 resiliently biases piston valve body 36 into damped engagement with valve stop 44 whenever piston valve body 36 is in the second sub-interval.
  • Valve stop 44 includes a valve stop base 78 and a valve stop head 80.
  • a pin 82 retains valve stop head 80.
  • Second control valve spring 76 encircles pin 82 and is held between valve stop base 78 and the valve stop head 80.
  • an engagement surface 86 engages a reciprocal drive member, such as a cam 88.
  • the reciprocal motion imparted to engagement surface 86 is transferred to plunger 26 in a conventional manner.
  • piston valve body 36 is axially movable over the motion displacement interval between the first and second positions.
  • Piston valve body 36 includes a piston valve body seat 90.
  • Seat 90 contacts a pump body seating surface 91 whenever piston valve body 36 is in the first position and contacts valve stop head 80 whenever piston valve body 36 is in the second position.
  • First control valve spring 70 is resiliently biasing the piston valve body 36 toward the unactuated position whenever piston valve body 36 is in the first sub-interval of the motion displacement interval.
  • Second control valve spring 76 resiliently biases piston valve body 36 toward either the first position or the second position so as to resiliently bias piston valve body 36 into damped engagement with valve stop 44 whenever piston valve body 36 is in the second sub-interval of the motion displacement interval.
  • first control valve spring 70 resiliently biases piston valve body 36 toward the unactuated position, that is, toward valve stop head 80.
  • Second control valve spring 76 resiliently biases piston valve body 36 to slow and dampen the engagement of piston valve body 36 with valve stop head 80.
  • a pump body 92 has a fuel inlet 94, a control valve chamber 96, and passageways 98 and 100 for fuel flow.
  • a control valve 102 having a piston valve body 104 is disposed in control valve chamber 96. Passageways 106 are provided for fuel flow.
  • An armature 108 is secured to control valve 102 by a fastener, such as a screw 110.
  • a valve stop 112 is disposed in pump body 92 adjacent control valve chamber 96. Piston valve body 104 contacts valve stop 112 whenever piston valve body 104 is in the second position, as shown in the lower half of Figure 3.
  • An O-ring 114 encircles valve stop 112.
  • a stop plate 116 secures valve stop 112 within pump body 92.
  • a stator spacer 118 has a central opening 120 for receiving armature 108 therein.
  • Stator spacer 118 has notches 122 for receiving a retainer 124.
  • O-rings 126 seal stator spacer 118 against pump body 92 and stator assembly 30.
  • a first control valve spring 128 resiliently biases piston valve body 104 toward valve stop 112.
  • a seat 130 is provided for first control valve spring 128.
  • Second control valve spring 132 is concentrically disposed with first spring 128 and resiliently biases piston valve body 104 toward valve stop 112. Second control valve spring 132 is provided with a seat 134 on the control valve 102.
  • the second position for piston valve body 104 is the unactuated position.
  • the first control valve spring 128 resiliently biases piston valve body 104 toward the unactuated position, that is, toward valve stop 112.
  • Seat 130 is shaped so that first control valve spring 128 biases piston valve body 104 whenever piston valve body 104 is in the first sub-interval.
  • the second control valve spring 132 resiliently biases piston valve body 104 toward valve stop 112 to slow and dampen the engagement of piston valve body 104 with valve stop 112.
  • Seat 134 is shaped so that the second control valve spring 132 always biases piston valve body 104 in the first and second sub-intervals.
  • a pump body 140 has a control valve chamber 142, and passageways 144 and 146.
  • a control valve 148 having a piston valve body 150 is disposed in control valve chamber 142. Passageways 152 are provided for fluid flow.
  • a valve stop 156 is disposed in pump body 140 adjacent control valve chamber 142.
  • An O-ring 158 encircles valve stop 156.
  • a stop plate 160 secures valve stop 156 within pump body 140.
  • a second control valve spring 162 is disposed within piston valve body 150. Second control valve spring 162 has a seat 164.
  • the flow passage may be provided by boring the piston 154 from one end only and provided radial directed flow passages 165 in fluid communication with the bore 163.
  • a pump body 170 has a control valve chamber 172, and passageways 174 and 176.
  • a control valve 178 having a piston valve body 180 is disposed in control valve chamber 172. Passageways 182 are provided for fluid flow.
  • a cylindrical valve stop 184 is disposed in pump body 170.
  • An O-ring 186 encircles valve stop 184.
  • a stop plate 188 secures valve stop 184 within pump body 170.
  • Passageway 190 is provided in valve stop 184 for fluid flow.
  • a second control valve spring 192 is provided for dampening the engagement of piston valve body 180 with valve stop 184.
  • a seat 194 abuts an end of second control valve spring 192.
  • Pump 10 Operation of pump 10 will now be described with reference to Figure 1. Fuel is received from a fuel supply by fuel inlet 16. The cam 88 drives engagement surface 86. Plunger 26 is moved from the retracted position B to the extended position A, and fuel is pressurized within pumping chamber 14.
  • Control valve 34 is controlled by electromagnetic actuator 32, and allows pressurized fuel to be directed through outlet port 18 by way of passageways 22 and 24.
  • FIG. 6a there is shown a graph of piston valve body displacement versus time during operation of the control valve assembly according to a method of the prior art.
  • the piston valve body seat contacts the pump body seating surface.
  • the piston valve body seat contacts the valve stop.
  • the solenoid current is discontinued and the piston valve body is urged from the full closed position toward the full open position, initially contacting valve stop at time t 2 , experiencing thereafter some degree of bounce off the valve stop in cyclic diminishing fashion as shown.
  • the second control valve spring comes into play, either exclusively as shown in Figure 6b or jointly with the first valve spring, as shown in Figure 6c, thereby urging the piston valve body into a delayed, damped engagement with the valve stop.
  • valve "bounce" is observed as the piston valve body settles into engagement with the valve stop.
  • the mechanical control valve assembly can be modeled electrically. Further, damping of the control valve at one or both ends of its stroke is controlled electronically by adjusting current levels to the control valve armature coil and the one of this control technique particularly in pilot injection type fuel injection systems thereby facilitating precise control over the initiation of the pilot injection by the precise control of the end of the preceding main injection illustrated as t 2 in Figures 6b and 6c.
  • the piston valve body In the first sub-interval, the piston valve body is held in the first position either by the first control valve spring or the induced force from the electromagnetic actuator. If the piston valve body is held in the first position by the first control valve spring, then by actuation of the electromagnetic actuator, the piston valve body is urged toward the second position. If the piston valve body is held in the first position by the induced force from the electromagnetic actuator, then the piston valve body is urged toward the second position by the first control valve spring upon deactuation. As the piston valve body approaches the second position in either one of the previously described manners, the piston valve body moves through the first sub-interval.
  • the piston valve body Upon entering the second sub-interval, the piston valve body is in close proximity with the valve stop.
  • the second control valve spring being configured to apply force in the appropriate direction to bring the piston valve body into dleayed engagement with the valve stop, resiliently biases the piston valve body.
  • the control valve assembly can be provided with the piston-auxiliary fuel flow arrangement, or further controlled electrically.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (21)

  1. Pumpe (10) für ein Kraftstoff-Einspritzsystem, umfassend:
    einen Pumpenkörper (12) mit einer Pumpenkammer (14), einem Kraftstoffeinlaß (16) zum Zuführen von Kraftstoff in die Pumpenkammer (14), eine Auslaßöffnung (18), und eine Steuerventilkammer (20) zwischen der Pumpenkammer und der Auslaßöffnung (18);
    einen in der Pumpenkammer (20) angeordneten Hubkolben (26), der über eine Hubspanne zwischen einer ausgefahrenen Stellung (A) und einer zurückgezogenen Stellung (B) hin- und herbewegbar ist;
    eine Kolbenfeder (28) zum elastischen Vorspannen des Kolbens (26) in die zurückgezogene Stellung (B);
    ein antreibbares Steuerventil (34) zum Steuern von Kraftstoff, wobei das Steuerventil (34) in der Steuerventilkammer (20) angeordnet ist, und das Steuerventil (34) einen Kolbenschieber (36) hat, der in der Steuerventilkammer (20) axial über eine Hubspanne von einer ersten Stellung in eine zweite Stellung bewegbar ist, wobei die Hubspanne definiert ist durch eine erste und eine zweite Hub-Unterspanne, die von der ersten, bzw. zweiten Stellung begrenzt wird;
    eine Statoranordnung (30);
    einen elektromagnetischen Antrieb (32) zum Antreiben des Steuerventils (34), wobei der elektromagnetische Antrieb (32) in der Statoranordnung (30) angeordnet ist, und wobei der Kolbenschieber (36) in einen Antriebszustand geführt wird, wenn das Steuerventil (34) in einem Antriebszustand ist, welcher der ersten oder der zweiten Stellung entspricht, wohingegen eine Nicht-Antriebsstellung der anderen der ersten oder zweiten Stellung entspricht;
    einen Anker (108), der an dem Steuerventil (34) befestigt ist;
    einem in dem Pumpenkörper (12) angrenzend an die Steuerventilkammer (20) angeordneten Ventilanschlag (44), wobei der Kolbenschieber (36) den Ventilanschlag (44) berührt, wenn der Kolbenschieber (36) in der zweiten Stellung ist;
    eine erste Steuerventilfeder (70) zum elastischen Vorspannen des Kolbenschiebers (36) in die Nicht-Antriebsstellung, wenn der Kolbenschieber (36) in der ersten Hub-Unterspanne ist; und
    eine Anschlagplatte, die den Ventilanschlag (44) in dem Pumpenkörper (12) befestigt; dadurch gekennzeichnet, daß
    eine zweite Steuerventilfeder (76) zum elastischen Vorspannen des Kolbenschiebers (36) in einen gedämpften Eingriff mit dem Ventilanschlag, wenn der Kolbenschieber in der zweiten Hub-Unterspanne ist;
    ein Stator-Beabstandungselement (50), das zwischen dem Pumpenkörper (12) und der Statoranordnung (30) angeordnet ist und eine zentrale Öffnung (52) hat zum Aufnehmen des Ankers (108); und
    mehrere Verbindungselemente (60) zum Montieren der Statoranordnung (30) und des Stator-Beabstandungselements (50) an dem Pumpenkörper (12), wobei der Kolbenschieber (36) bei Antrieb des Steuerventils (34) entgegen der Vorspannung der ersten Steuerventilfeder (70) in die Antriebsstellung geführt wird.
  2. Pumpe (10) nach Anspruch 1, wobei die Antriebsstellung die erste Stellung ist, und wobei der Kolbenschieber (36) bei Nicht-Antrieb des Steuerventils in die Nicht-Antriebsstellung und in gedämpften Eingriff mit dem Ventilanschlag (44) geführt wird.
  3. Pumpe (10) nach Anspruch 1, wobei die Antriebsstellung die zweite Stellung ist, und wobei der Kolbenschieber bei Antrieb des Steuerventils in die Antriebsstellung und in gedämpften Eingriff mit dem Ventilanschlag (112) geführt wird.
  4. Pumpe nach Anspruch 1, wobei die erste Steuerventilfeder (70) den Kolbenschieber (36) elastisch in die zweite Stellung vorspannt, wenn der Kolbenschieber (36) in der zweiten Hub-Unterspanne ist.
  5. Pumpe nach Anspruch 1, wobei die zweite Steuerventilfeder den Kolbenschieber elastisch in die erste Position vorspannt, wenn der Kolbenschieber in der zweiten Hub-Unterspanne ist.
  6. Pumpe nach Anspruch 1, wobei die zweite Steuerventilfeder den Kolbenschieber elastisch in die zweite Position vorspannt, wenn der Kolbenschieber in der zweiten Hub-Unterspanne ist.
  7. Pumpe nach Anspruch 1, wobei die Steuerventilfeder den Kolbenschieber elastisch in einen gedämpften Eingriff mit dem Ventilanschlag vorspannt, wenn der Kolbenschieber in der ersten Hub-Unterspanne ist.
  8. Pumpe nach Anspruch 1, wobei die Steuerventilfeder von dem Ventilanschlag umgeben ist.
  9. Pumpe (10) nach Anspruch 1, ferner umfassend:
    einen in dem Kolbenschieber (150) aufgenommenen Kolben (154) mit einem ersten und einem zweiten Ende sowie einer Umfangsfläche, wobei das erste Ende an den Ventilanschlag (156) angrenzt und das zweite Ende an ein Ende der zweiten Steuerventilfeder (162) angrenzt, und wobei die zweiten Steuerventilfeder (162) in dem Kolbenschieber (150) aufgenommen ist und der Kolben (154) einen Durchfluß (155) hat, der das Durchströmen von Kraftstoff ermöglicht und an der Umfangsfläche des Kolbens (154) ausgebildet ist, und wobei sich der Durchfluß (155) von dem zweiten Ende zum ersten Ende erstreckt und sich der Durchfluß (155) außerhalb des Kolbenschiebers (150) erstreckt, wenn der Kolbenschieber (150) in der Hub-Unterspanne ist und der Durchfluß (155) von dem Kolbenschieber (150) umgeben ist, wenn der Kolbenschieber (150) in der zweiten Hub-Unterspanne ist und wobei der Kraftstofffluß reduziert ist, wenn der Durchfluß (155) von dem Kolbenschieber (150) umgeben ist, wodurch der Eingriff des Kolbenschiebers (150) mit dem Ventilanschlag (156) gedämpft wird.
  10. Steuerventilanordnung, umfassend:
    ein Gehäuse mit einer Steuerventilkammer (142);
    ein in der Steuerventilkammer (142) angeordnetes Steuerventil (148), das einen Kolbenschieber (150) umfaßt, der in der Steuerventilkammer (142) axial über eine Hubspanne von einer ersten Stellung in eine zweite Stellung bewegbar ist, wobei die Hubspanne definiert ist durch eine erste und eine zweite Hub-Unterspanne, die von der ersten, bzw. zweiten Stellung begrenzt wird;
    einen Ventilanschlag (156), der in dem Gehäuse angrenzend an die Steuerventilkammer (142) angeordnet ist, wobei der Kolbenschieber (150) den Ventilanschlag (156) berührt, wenn der Kolbenschieber (150) in der zweiten Stellung ist;
    eine erste Steuerventilfeder zum elastischen Vorspannen des Kolbenschiebers (150) in die zweite Stellung, wenn der Kolbenschieber (150) in der ersten Hub-Unterspanne ist;
    eine zweite Steuerventilfeder (162) zum elastischen Vorspannen des Kolbenschiebers (150) in gedämpften Eingriff mit dem Ventilanschlag (156), wenn der Kolbenschieber (150) in der zweiten Hub-Unterspanne ist; und gekennzeichnet durch
    einen Kolben (154), der in dem Kolbenschieber (150) aufgenommen ist und ein erstes und ein zweites Ende sowie eine Umfangsfläche hat, wobei das erste Ende an den Ventilanschlag (156) angrenzt und das zweite Ende an ein Ende der zweiten Steuerventilfeder (162) angrenzt, und wobei die zweite Steuerventilfeder (162) in dem Kolbenschieber (150) aufgenommen ist und der Kolben (154) einen Durchfluß (155) hat, der das Durchströmen von Kraftstoff ermöglicht und an der Umfangsfläche des Kolbens (154) ausgebildet ist, und wobei sich der Durchfluß (155) von dem zweiten Ende zum ersten Ende erstreckt und sich der Durchfluß (155) außerhalb des Kolbenschiebers (150) erstreckt, wenn der Kolbenschieber (150) in der Hub-Unterspanne ist und der Durchfluß (155) von dem Kolbenschieber (150) umgeben ist, wenn der Kolbenschieber (150) in der zweiten Hub-Unterspanne ist und der Fluidfluß reduziert ist, wenn der Durchfluß (155) von dem Kolbenschieber (150) umgeben ist, wodurch der Eingriff des Kolbenschiebers (150) mit dem Ventilanschlag (156) gedämpft wird.
  11. Steuerventilanordnung nach Anspruch 10, wobei die erste Steuerventilfeder den Kolbenschieber elastisch in die zweite Stellung vorspannt, wenn der Kolbenschieber in der zweiten Hub-Unterspanne ist.
  12. Steuerventilanordnung nach Anspruch 10, wobei die zweite Steuerventilfeder den Kolbenschieber elastisch in die erste Position vorspannt, wenn der Kolbenschieber in der zweiten Hub-Unterspanne ist.
  13. Steuerventilanordnung nach Anspruch 10, wobei die zweite Steuerventilfeder den Kolbenschieber elastisch in die zweite Position vorspannt, wenn der Kolbenschieber in der zweiten Hub-Unterspanne ist.
  14. Steuerventilanordnung nach Anspruch 10, wobei die Steuerventilfeder den Kolbenschieber elastisch in einen gedämpften Eingriff mit dem Ventilanschlag vorspannt, wenn der Kolbenschieber in der ersten Hub-Unterspanne ist.
  15. Steuerventilanordnung nach Anspruch 10, ferner umfassend:
    Mittel zum Antreiben des Steuerventils, wobei der Kolbenschieber (150) in eine Antriebsstellung geführt wird, wenn das Steuerventil (148) in einem Antriebszustand ist, welcher der ersten oder der zweiten Stellung entspricht, wohingegen eine Nicht-Antriebsstellung der anderen der ersten oder zweiten Stellung entspricht.
  16. Steuerventilanordnung nach Anspruch 15, wobei die Antriebsstellung die erste Stellung ist, und wobei der Kolbenschieber (150) bei Nicht-Antrieb des Steuerventils in die Nicht-Antriebsstellung und in gedämpften Eingriff mit dem Ventilanschlag (156) geführt wird.
  17. Steuerventilanordnung nach Anspruch 15, wobei die Antriebsstellung die zweite Stellung ist, und wobei der Kolbenschieber (150) bei Antrieb des Steuerventils in die Antriebsstellung und in gedämpften Eingriff mit dem Ventilanschlag (156) geführt wird.
  18. Steuerventilanordnung nach Anspruch 15, wobei die erste Steuerventilfeder den Kolbenschieber elastisch in die zweite Stellung vorspannt, wenn der Kolbenschieber in der zweiten Hub-Unterspanne ist.
  19. Steuerventilanordnung nach Anspruch 15, wobei die zweite Steuerventilfeder den Kolbenschieber elastisch in die erste Position vorspannt, wenn der Kolbenschieber in der zweiten Hub-Unterspanne ist.
  20. Steuerventilanordnung nach Anspruch 15, wobei die zweite Steuerventilfeder den Kolbenschieber elastisch in die zweite Position vorspannt, wenn der Kolbenschieber in der zweiten Hub-Unterspanne ist.
  21. Pumpe nach Anspruch 15, wobei die zweite Steuerventilfeder den Kolbenschieber elastisch in einen gedämpften Eingriff mit dem Ventilanschlag vorspannt, wenn der Kolbenschieber in der ersten Hub-Unterspanne ist.
EP96914714A 1995-06-23 1996-05-20 Brennstoffpumpe Expired - Lifetime EP0834013B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US49394995A 1995-06-23 1995-06-23
US493949 1995-06-23
PCT/US1996/007246 WO1997001031A1 (en) 1995-06-23 1996-05-20 Fuel pump and method of operating same

Publications (3)

Publication Number Publication Date
EP0834013A1 EP0834013A1 (de) 1998-04-08
EP0834013A4 EP0834013A4 (de) 1999-09-22
EP0834013B1 true EP0834013B1 (de) 2002-10-09

Family

ID=23962383

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96914714A Expired - Lifetime EP0834013B1 (de) 1995-06-23 1996-05-20 Brennstoffpumpe

Country Status (4)

Country Link
EP (1) EP0834013B1 (de)
JP (1) JPH11508345A (de)
DE (1) DE69624240T2 (de)
WO (1) WO1997001031A1 (de)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5954487A (en) * 1995-06-23 1999-09-21 Diesel Technology Company Fuel pump control valve assembly
GB9720003D0 (en) * 1997-09-20 1997-11-19 Lucas Ind Plc Drive circuit
DE19809627A1 (de) * 1998-03-06 1999-09-09 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE19843546A1 (de) * 1998-09-23 2000-03-30 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
US6276610B1 (en) 1998-12-11 2001-08-21 Diesel Technology Company Control valve
US6158419A (en) * 1999-03-10 2000-12-12 Diesel Technology Company Control valve assembly for pumps and injectors
US6089470A (en) * 1999-03-10 2000-07-18 Diesel Technology Company Control valve assembly for pumps and injectors
DE19923422C2 (de) * 1999-05-21 2003-05-08 Bosch Gmbh Robert Elektronisches Einspritzsystem
DE19939459A1 (de) * 1999-08-20 2000-11-23 Bosch Gmbh Robert Hydraulischer Druckerzeuger
DE19956519B4 (de) * 1999-11-24 2004-05-27 Robert Bosch Gmbh Vorrichtung zum Einspritzen eines Fluides mit variablem Einspritzdruck
DE10017060B4 (de) 2000-04-05 2005-05-19 Daimlerchrysler Ag Verfahren zum Betreiben einer Diesel-Brennkraftmaschine mit einem Pumpe-Leitung-Düse-Einspritzsystem
US6450778B1 (en) 2000-12-07 2002-09-17 Diesel Technology Company Pump system with high pressure restriction
JP2013053545A (ja) * 2011-09-02 2013-03-21 Yanmar Co Ltd 燃料噴射ポンプ
JP6547564B2 (ja) * 2015-09-30 2019-07-24 ヤンマー株式会社 電磁スピル弁

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2770394A (en) * 1954-05-04 1956-11-13 Automatic Canteen Co Method and apparatus for dispensing a measured amount of beverage ingredients
JPS5624108B2 (de) * 1974-06-14 1981-06-04
DE3128975A1 (de) 1981-07-22 1983-02-10 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe
US4569641A (en) * 1982-09-07 1986-02-11 Greatbatch Enterprises, Inc. Low power electromagnetic pump
DE3302294A1 (de) * 1983-01-25 1984-07-26 Klöckner-Humboldt-Deutz AG, 5000 Köln Kraftstoffeinspritzvorrichtung fuer luftverdichtende, selbstzuendende brennkraftmaschinen
US4618095A (en) 1985-07-02 1986-10-21 General Motors Corporation Electromagnetic unit fuel injector with port assist spilldown
DE3601710C2 (de) * 1986-01-22 1998-07-02 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
GB8829902D0 (en) * 1988-12-22 1989-02-15 Lucas Ind Plc Control circuit
DE4020951A1 (de) * 1990-06-30 1992-01-02 Bosch Gmbh Robert Magnetventil
GB9422742D0 (en) * 1994-11-11 1995-01-04 Lucas Ind Plc Drive circuit

Also Published As

Publication number Publication date
JPH11508345A (ja) 1999-07-21
EP0834013A4 (de) 1999-09-22
EP0834013A1 (de) 1998-04-08
DE69624240T2 (de) 2003-06-18
DE69624240D1 (de) 2002-11-14
WO1997001031A1 (en) 1997-01-09

Similar Documents

Publication Publication Date Title
US5954487A (en) Fuel pump control valve assembly
EP0834013B1 (de) Brennstoffpumpe
CA1228517A (en) Electromagnetic unit fuel injector
US6056264A (en) Solenoid actuated flow control valve assembly
US4540155A (en) Fluid control valves
JPH07332197A (ja) 複式ソレノイドを有する燃料噴射制御弁
JPS62113862A (ja) 電磁制御弁および内燃機関用燃料噴射装置
EP0850356A1 (de) Brennstoffeinspritzpumpe mit magnetventil
US4573659A (en) Fluid control valve
EP1165957B1 (de) Regelventilanordnung für pumpen und injektoren
JP2002522706A (ja) コントロールバルブ
WO1999015780A1 (en) Control valve having a solenoid with a permanent magnet for a fuel injector
WO1999015781A1 (en) Control valve having a top mounted single pole solenoid for a fuel injector
EP1149235B1 (de) Regelventil
US6158419A (en) Control valve assembly for pumps and injectors
GB2169385A (en) Solenoid valve for controlling fluid
US6702207B2 (en) Fuel injector control module with unidirectional dampening
EP1093543B1 (de) Flexible anschlüsse für das kontrollventil eines brennstoffeinspritzsystems
US6758416B2 (en) Fuel injector having an expansion tank accumulator
GB2135758A (en) Fluid control valve
US5449119A (en) Magnetically adjustable valve adapted for a fuel injector

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19980116

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

A4 Supplementary search report drawn up and despatched

Effective date: 19990811

AK Designated contracting states

Kind code of ref document: A4

Designated state(s): DE FR GB IT

RIC1 Information provided on ipc code assigned before grant

Free format text: 6F 04B 7/00 A, 6F 02M 59/46 B, 6F 02M 59/36 B

17Q First examination report despatched

Effective date: 20010508

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

RTI1 Title (correction)

Free format text: FUEL PUMP

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 69624240

Country of ref document: DE

Date of ref document: 20021114

ET Fr: translation filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20030529

Year of fee payment: 8

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20030710

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040130

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20041201

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050520

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20060524

Year of fee payment: 11

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20070520

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070520