WO1997001031A1 - Pompe a carburant et son procede de fonctionnement - Google Patents

Pompe a carburant et son procede de fonctionnement Download PDF

Info

Publication number
WO1997001031A1
WO1997001031A1 PCT/US1996/007246 US9607246W WO9701031A1 WO 1997001031 A1 WO1997001031 A1 WO 1997001031A1 US 9607246 W US9607246 W US 9607246W WO 9701031 A1 WO9701031 A1 WO 9701031A1
Authority
WO
WIPO (PCT)
Prior art keywords
control valve
piston
valve body
piston valve
interval
Prior art date
Application number
PCT/US1996/007246
Other languages
English (en)
Inventor
Robert D. Straub
Werner Faupel
Original Assignee
Diesel Technology Company
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 Company filed Critical Diesel Technology Company
Priority to JP9503837A priority Critical patent/JPH11508345A/ja
Priority to DE69624240T priority patent/DE69624240T2/de
Priority to EP96914714A priority patent/EP0834013B1/fr
Publication of WO1997001031A1 publication Critical patent/WO1997001031A1/fr

Links

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 may stop, the control valve "bounce" of 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 t 2 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.
  • ⁇ 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.
  • the piston valve body Upon deactuation of the control valve, the piston valve body is urged toward the second position, and into damped engagement with the valve stop.
  • first and second control valve springs in accordance with the present invention.
  • the first control valve spring could altematively 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. When the flow passage is enclosed by the piston valve body, fluid flow is restricted thereby dampening the engagement of the piston valve body with said valve stop.
  • control valve assembly or method of the present invention can be used in pumps or injectors having either a vertical or horizontal orientated plunger.
  • FIGURE 1 is a side elevation, partially in section, of a pump for a fuel injection system, the pump having a first embodiment of a control valve assembly made in accordance with the present invention
  • FIGURE 2 is an enlarged cross-sectional view of the control valve assembly of Figure 1;
  • FIGURE 3 is an enlarged cross-sectional view of a second embodiment of a control valve assembly of the present invention, and showing the valve in open position (lower half) and closed (upper half) ,-
  • FIGURE 4a is an enlarged cross-sectional view of a third embodiment of a control valve assembly of the present invention.
  • FIGURE 4b is an enlarged cross-sectional view of the piston shown in Figure 4a, taken along line X-X of Figure 4a;
  • FIGURE 4c is a side elevation view of an alternative piston as may be employed in the embodiment of Figure 4a;
  • FIGURE 4d is a cross-sectional view of the piston shown in Figure 4c, taken along line Y-Y of Figure 4c;
  • FIGURE 5 is an enlarged cross-sectional view of a fourth embodiment of a control valve assembly of the present invention
  • FIGURE 6a is a graph illustrating piston valve body displacement versus time during operation of a control valve assembly according to a method of the prior art
  • FIGURES 6b and 6c is the present invention as depicted by all its embodiments, including the mechanical control arrangements of Figures 2-5, and the electronic control arrangement described herein.
  • 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.
  • 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 pisto 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
  • 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.
  • 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
  • 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
  • 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.
  • damping of the control valve at one or both ends of its stroke is controllec 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)

Abstract

Cette invention concerne une pompe à carburant (10) qui est destinée à un système de pompe à carburant d'un véhicule diesel, et qui comporte un dispositif de clapet de commande, lequel comprend un boîtier dans lequel, se trouve une chambre (20) de clapet de commande, ainsi qu'un clapet de commande (34) fonctionnel se trouvant dans ladite chambre (20) du clapet de commande. Ce clapet de commande comprend un corps de clapet à piston (36) pouvant se déplacer axialement sur un intervalle de course entre une première et une seconde positions. Cet intervalle de course est défini par un premier et un second sous-intervalle, eux-mêmes délimités par les première et seconde positions, respectivement. Ce dispositif de clapet de commande comprend également un système d'actionnement (32) du clapet de commande. Une butée (44) de clapet est située dans le boîtier en position adjacente par rapport à la chambre (20) du clapet de commande, tandis qu'un siège (90) du corps du clapet à piston entre en contact avec ladite butée (44) de clapet lorsque le corps (36) du clapet à piston se trouve dans la seconde position. Lorsque le corps du clapet à piston se trouve dans la première position, le siège (90) du corps du clapet à piston entre en contact avec une surface de siège du corps de la pompe.
PCT/US1996/007246 1995-06-23 1996-05-20 Pompe a carburant et son procede de fonctionnement WO1997001031A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP9503837A JPH11508345A (ja) 1995-06-23 1996-05-20 燃料ポンプおよびその作動方法
DE69624240T DE69624240T2 (de) 1995-06-23 1996-05-20 Brennstoffpumpe
EP96914714A EP0834013B1 (fr) 1995-06-23 1996-05-20 Pompe a carburant

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US49394995A 1995-06-23 1995-06-23
US493,949 1995-06-23

Publications (1)

Publication Number Publication Date
WO1997001031A1 true WO1997001031A1 (fr) 1997-01-09

Family

ID=23962383

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1996/007246 WO1997001031A1 (fr) 1995-06-23 1996-05-20 Pompe a carburant et son procede de fonctionnement

Country Status (4)

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

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2335007A (en) * 1998-03-06 1999-09-08 Bosch Gmbh Robert Fuel-injection device for internal combustion engines
WO2000017511A1 (fr) * 1998-09-23 2000-03-30 Robert Bosch Gmbh Dispositif d'injection de carburant destine a des moteurs a combustion interne
US6059545A (en) * 1995-06-23 2000-05-09 Diesel Technology Company Fuel pump control valve assembly
WO2000034644A1 (fr) 1998-12-11 2000-06-15 Diesel Technology Company Soupape de regulation
US6089470A (en) * 1999-03-10 2000-07-18 Diesel Technology Company Control valve assembly for pumps and injectors
GB2350154A (en) * 1999-05-21 2000-11-22 Bosch Gmbh Robert Fuel injection system with solenoid valve in high-pressure pump cylinder
DE19939459A1 (de) * 1999-08-20 2000-11-23 Bosch Gmbh Robert Hydraulischer Druckerzeuger
US6158419A (en) * 1999-03-10 2000-12-12 Diesel Technology Company Control valve assembly for pumps and injectors
US6450778B1 (en) 2000-12-07 2002-09-17 Diesel Technology Company Pump system with high pressure restriction
US6457457B1 (en) * 1997-09-20 2002-10-01 Delphi Technologies, Inc. Control method
US6523526B2 (en) 2000-04-05 2003-02-25 Daimler Chrysler Ag Method for operating a diesel engine with a pump-line-nozzle injection system

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19956519B4 (de) * 1999-11-24 2004-05-27 Robert Bosch Gmbh Vorrichtung zum Einspritzen eines Fluides mit variablem Einspritzdruck
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

Citations (5)

* 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
US3958902A (en) * 1974-06-14 1976-05-25 Taisan Industrial Co., Ltd. Electromagnetic pump
US4501246A (en) 1981-07-22 1985-02-26 Robert Bosch Gmbh Fuel injection pump
US4569641A (en) * 1982-09-07 1986-02-11 Greatbatch Enterprises, Inc. Low power electromagnetic pump
US4618095A (en) 1985-07-02 1986-10-21 General Motors Corporation Electromagnetic unit fuel injector with port assist spilldown

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3302294A1 (de) * 1983-01-25 1984-07-26 Klöckner-Humboldt-Deutz AG, 5000 Köln Kraftstoffeinspritzvorrichtung fuer luftverdichtende, selbstzuendende brennkraftmaschinen
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

Patent Citations (5)

* 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
US3958902A (en) * 1974-06-14 1976-05-25 Taisan Industrial Co., Ltd. Electromagnetic pump
US4501246A (en) 1981-07-22 1985-02-26 Robert Bosch Gmbh Fuel injection pump
US4569641A (en) * 1982-09-07 1986-02-11 Greatbatch Enterprises, Inc. Low power electromagnetic pump
US4618095A (en) 1985-07-02 1986-10-21 General Motors Corporation Electromagnetic unit fuel injector with port assist spilldown

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP0834013A4 *

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6059545A (en) * 1995-06-23 2000-05-09 Diesel Technology Company Fuel pump control valve assembly
US6457457B1 (en) * 1997-09-20 2002-10-01 Delphi Technologies, Inc. Control method
FR2775737A1 (fr) * 1998-03-06 1999-09-10 Bosch Gmbh Robert Dispositif d'injection de carburant pour moteur a combustion interne
GB2335007B (en) * 1998-03-06 2000-03-29 Bosch Gmbh Robert Fuel-injection device for internal combustion engines
GB2335007A (en) * 1998-03-06 1999-09-08 Bosch Gmbh Robert Fuel-injection device for internal combustion engines
WO2000017511A1 (fr) * 1998-09-23 2000-03-30 Robert Bosch Gmbh Dispositif d'injection de carburant destine a des moteurs a combustion interne
WO2000034644A1 (fr) 1998-12-11 2000-06-15 Diesel Technology Company Soupape de regulation
EP1149235A1 (fr) * 1998-12-11 2001-10-31 Diesel Technology Company Soupape de regulation
EP1149235B1 (fr) * 1998-12-11 2012-05-02 Diesel Technology Company Soupape de regulation
JP2002539360A (ja) * 1999-03-10 2002-11-19 ディーゼル・テクノロジー・カンパニー ポンプおよび噴射器のための制御バルブ組立体
US6158419A (en) * 1999-03-10 2000-12-12 Diesel Technology Company Control valve assembly for pumps and injectors
EP1165957A1 (fr) * 1999-03-10 2002-01-02 Diesel Technology Company Ensemble de soupapes de distribution pour pompes et injecteurs
US6089470A (en) * 1999-03-10 2000-07-18 Diesel Technology Company Control valve assembly for pumps and injectors
EP1165957A4 (fr) * 1999-03-10 2004-03-03 Diesel Tech Co Ensemble de soupapes de distribution pour pompes et injecteurs
JP2001003838A (ja) * 1999-05-21 2001-01-09 Robert Bosch Gmbh 電子式の噴射機構
GB2350154B (en) * 1999-05-21 2001-07-18 Bosch Gmbh Robert Electronic injection system
GB2350154A (en) * 1999-05-21 2000-11-22 Bosch Gmbh Robert Fuel injection system with solenoid valve in high-pressure pump cylinder
JP4612149B2 (ja) * 1999-05-21 2011-01-12 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング 電子式の噴射機構
DE19939459A1 (de) * 1999-08-20 2000-11-23 Bosch Gmbh Robert Hydraulischer Druckerzeuger
US6523526B2 (en) 2000-04-05 2003-02-25 Daimler Chrysler Ag Method for operating a diesel engine with a pump-line-nozzle injection system
US6450778B1 (en) 2000-12-07 2002-09-17 Diesel Technology Company Pump system with high pressure restriction
US6854962B2 (en) 2000-12-07 2005-02-15 Robert Bosch Gmbh Pump system with high pressure restriction

Also Published As

Publication number Publication date
DE69624240D1 (de) 2002-11-14
EP0834013B1 (fr) 2002-10-09
EP0834013A1 (fr) 1998-04-08
JPH11508345A (ja) 1999-07-21
DE69624240T2 (de) 2003-06-18
EP0834013A4 (fr) 1999-09-22

Similar Documents

Publication Publication Date Title
US6059545A (en) Fuel pump control valve assembly
EP0834013B1 (fr) Pompe a carburant
US6308690B1 (en) Hydraulically controllable camless valve system adapted for an internal combustion engine
CA1228517A (fr) Systeme d'injection indirecte a soupape electromagnetique
US5749717A (en) Electromagnetic fuel pump for a common rail fuel injection system
JPH07332197A (ja) 複式ソレノイドを有する燃料噴射制御弁
US4580760A (en) Fluid control valves
EP1076769A1 (fr) Injecteur hydraulique sans ressort
JP2002522706A (ja) コントロールバルブ
EP1165957B1 (fr) Ensemble de soupapes de distribution pour pompes et injecteurs
WO1999015780A1 (fr) Soupape de regulation comportant un solenoide pourvu d'un aimant permanent pour injecteur de carburant
EP1017939A1 (fr) Soupape de regulation comportant un solenoide unipolaire monte en tete pour injecteur de carburant
US6158419A (en) Control valve assembly for pumps and injectors
GB2169385A (en) Solenoid valve for controlling fluid
EP1093543B1 (fr) Armature flexible pour clapet de regulation de systeme d'injection de carburant
US6758416B2 (en) Fuel injector having an expansion tank accumulator
KR101890063B1 (ko) 디젤엔진 고압펌프의 유량 제어밸브
WO1996005424A1 (fr) Injecteur de carburant a siege de soupape a equilibrage des pressions
US5449119A (en) Magnetically adjustable valve adapted for a fuel injector

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): CA JP

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FI FR GB GR IE IT LU MC NL PT SE

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
ENP Entry into the national phase

Ref country code: JP

Ref document number: 1997 503837

Kind code of ref document: A

Format of ref document f/p: F

WWE Wipo information: entry into national phase

Ref document number: 1996914714

Country of ref document: EP

WWP Wipo information: published in national office

Ref document number: 1996914714

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: CA

WWG Wipo information: grant in national office

Ref document number: 1996914714

Country of ref document: EP