EP1314873A2 - Pompe à injection distributrice mécanique à accélération de démarrage à froid - Google Patents

Pompe à injection distributrice mécanique à accélération de démarrage à froid Download PDF

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Publication number
EP1314873A2
EP1314873A2 EP02022594A EP02022594A EP1314873A2 EP 1314873 A2 EP1314873 A2 EP 1314873A2 EP 02022594 A EP02022594 A EP 02022594A EP 02022594 A EP02022594 A EP 02022594A EP 1314873 A2 EP1314873 A2 EP 1314873A2
Authority
EP
European Patent Office
Prior art keywords
piston
spring
injection
pressure pump
cold start
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.)
Granted
Application number
EP02022594A
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German (de)
English (en)
Other versions
EP1314873B1 (fr
EP1314873A3 (fr
Inventor
Guenter Bofinger
David Banham
Volker Freudl
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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
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Publication of EP1314873A2 publication Critical patent/EP1314873A2/fr
Publication of EP1314873A3 publication Critical patent/EP1314873A3/fr
Application granted granted Critical
Publication of EP1314873B1 publication Critical patent/EP1314873B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/128—Varying injection timing by angular adjustment of the face-cam or the rollers support
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
    • F02M41/1405—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis
    • F02M41/1411—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis characterised by means for varying fuel delivery or injection timing
    • F02M41/1416—Devices specially adapted for angular adjustment of annular cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic
    • F02D2001/186—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic using a pressure-actuated piston for adjustment of a stationary cam or roller support

Definitions

  • the start of injection is particularly with self-igniting internal combustion engines, to the respective operating phase adapt the internal combustion engine.
  • In the cold running phase especially at Low outside temperatures make it necessary to use diesel distributor injection pumps Injection start to be adjusted earlier and therefore with regard to particle emission a low-emission and low-noise start and a subsequent zero-emission start To achieve cold running phase.
  • With increasing engine speed it is necessary to advance the start of delivery of the injection pump in order to To compensate injection and ignition delay caused time shift.
  • diesel fuel takes a certain amount of time to pass from liquid state to change into the gaseous state and in this state with the Combustion air to form an inflammable, self-igniting mixture at high pressure.
  • the time required for this between the start of injection and the start of combustion is at Auto-ignition internal combustion engines referred to as ignition delay. This will among other factors also determined by the ignitability of the diesel fuel (expressed by the cetane number), the achievable compression ratio ⁇ of the self-igniting Internal combustion engine and the quality of fuel atomization through the injector of the fuel injector.
  • the ignition delay in self-igniting internal combustion engines is usually in the order of 1 to 2 ms. During the Cold running phase at low outside temperatures extends this period, which leads to Soot formation from unburned fuel leads to the environment through the exhaust system arrives.
  • Another way to adjust the start of injection early is by rotating a component designed as a roller ring during the start and the cold-running phase of the self-igniting internal combustion engine, the injection adjuster piston and thus postponing the start of injection early.
  • Another on Mechanically feasible measure for cold start acceleration consists in to press on one side of the injection adjuster piston by means of an eccentric shaft and thereby displacing the injection adjuster piston in such a way that the injection begins postponed early.
  • an adjustment unit for shifting the injection curve effective to reach By moving the support point of one of the injection adjuster pistons directly acting spring element from a movable component to a in the starting phase stationary component can act on the injection adjuster piston Swinging of this piston between two stop surfaces can be prevented. Thereby on the one hand, an uncontrolled axial movement of the injection adjuster piston remains, which, on the other hand, has a favorable influence on its material wear with regard to friction.
  • two spring elements of different spring stiffnesses c 1 , c 2 can be arranged on a displaceably mounted spring support ring.
  • the spring stiffness c 1 is always chosen to be very small, the spring stiffness being responsible for the cold start, while the spring stiffness c 2 of the remaining spring element is designed for normal operation.
  • the spring element of the spring assembly acting on the injection adjuster piston is pre-tensioned, while the spring element associated with the cold start acceleration piston in untensioned situation.
  • the injection adjuster piston directly acting on the spring element and for support of the spring package in series connected spring elements can be on the inside of the Cold start accelerating piston formed a stepped arrangement of several contact surfaces are, the individual contact surfaces for the spring elements preferably as Ring surfaces are designed to run.
  • Figure 1 shows a high-pressure pump with advance unit, as from the prior art known.
  • the high-pressure pump 1 comprises a housing 2, on the underside of which an adjustment unit 5 is flanged to delay the start of injection.
  • the adjustment unit 5 for moving the time of injection comprises a two-part housing, with a housing joint 40 between the housing halves of the adjusting unit 5 and the housing 2 of the High pressure pump 1 a sealing plate is inserted.
  • the adjusting unit 5 for shifting the injection time comprises a shiftable one mounted injection adjuster piston 6. Inside the injection adjuster piston 6 a pivot bearing 7 is arranged, which for receiving a not shown in Figure 1 Lever serves. By means of this lever, a roller ring, not shown here, of a high-pressure pump can 1 can be adjusted within the housing 2 such that the start of injection of fuel is moved into the combustion chambers of an internal combustion engine.
  • This lever is also used as an adjustment bolt for a spray adjuster piston called the roller ring.
  • the lever received in the rotary bearing 7 of the injection adjuster piston 6 passes through one Opening 9 in the injection adjuster piston, which is dimensioned such that a pivoting movement the lever of the pivot bearing 7 within the injection adjuster piston 6 is possible.
  • the injection adjuster piston 6 is from a first, essentially in the vertical direction extending first inlet bore 10 and a substantially perpendicular to this second inlet bore 11 traversed.
  • the second inlet bore 11 opens into a control slide bore 13 which is substantially parallel to the axis of symmetry of the injection adjuster piston 6 runs.
  • In the control slide bore 13 is a piston-shaped Control slide 12 let in, on its end facing a cavity 24 with an enlarged output bore is provided.
  • the control slide 12 corresponds to a control piston and is used in combination with the injection adjuster piston 6 also referred to as a follower or servo spray adjuster piston. Between one across Axis of symmetry of the control slide 12 extending first channel 14 and one in the control slide 12 executed second channel 15 there is a connection, the second Channel 15 opens into the area of the control slide 12, which has an enlarged inner diameter is trained.
  • the control slide 12 is a slotted on its outer peripheral surface Washer 16 associated with the axial displacement path of the control slide 12 within the injection adjuster piston 6 defines the slotted The disk forms a stop 22 for the control slide 12.
  • the slotted disc 16 lies within a recess 19 of the injection adjuster piston 6 on the second end face 18 of the injection adjuster piston 6, while the first end face 17 of the injection adjuster piston 6 in the state shown in FIG. 1 a housing boundary wall of the adjusting unit 5 for shifting the injection timing assigns.
  • the regulating slide 12 On its end face facing a cavity 24, the regulating slide 12 comprises one Support disc 20, which serves as a contact surface for a control spring 31.
  • the control spring 31 is supported on the inside 26 of a cold start acceleration piston 23.
  • a disk 21 may be provided on the inside 26 of the cold start acceleration piston 23.
  • the inside 26 of the cold start acceleration piston 23 also serves as a stop surface for a first spring element 25, which is located on the inside 26 opposite Supported on an intermediate plate 30.
  • On the intermediate plate 30 On the intermediate plate 30 is a annular projection formed as a stop surface for the second end face 18th the injection adjuster piston 6 is used.
  • Between the first spring element 25 and the Control spring 31 is also a trailing piston / slider retaining spring 32 embedded.
  • the sleeve body 34 has a first sleeve body stop 36 and a second sleeve body stop 37 on.
  • the control slide / trailing piston retaining spring 32 is supported on the one hand on the first sleeve body stop 36 and on the other hand on the slotted disc 16 in the area of second end face 18 of the injection adjuster piston 6.
  • the cold-start acceleration piston 23 shown here is supported with its one End space 27 facing the pressure chamber 28 on one on the housing wall of the adjusting unit 5 trained stop 29.
  • On the peripheral surface of the cold start acceleration piston 23 is an annular groove 38, which with a drain hole 39 with communicates with the cavity 24 which is from the inside 26 of the cold start acceleration piston 23, the intermediate plate 30 and the second end face 18 of the injection adjuster piston 6 is limited in the region of the recess 19.
  • a disadvantage of this embodiment variant of a high pressure pump 1 for supply A fuel injection system with fuel is the fact that between the inside 26 of the cold start acceleration piston 23 and the first sleeve body stop 36 there is a gap 33.
  • This gap 33 causes gradual pressure build-up in the cavity 24 via the inlet bores 10 and 11, the first channel 14 and the second channel 15 and the inside of the sleeve body 34 and the openings 35 made therein an uncontrolled movement of the injection adjuster piston 6 can occur. So that is a stable adjustment in the lower speed range of the high pressure pump 1 is difficult achievable since between the first sleeve body stop 36 and the opposite one Section of the inside 26 of the cold start acceleration piston 23 a design-related Free space remains. Since the second sleeve body stop 37 the support disc 20 of the control slide 12, the position of the first sleeve body stop lies 36 of the sleeve body 34 firmly, thereby forming the annular gap 33 comes.
  • Figure 2 shows an adjustment unit for shifting the start of injection in longitudinal section.
  • the housing 2 of a high-pressure pump 1 is one Adjustment unit 5 assigned to shift the injection timing.
  • a Injection adjuster piston 6 is included, which comprises a rotary bearing 7, in which a Lever element 8, not shown here, is included, which has a roller ring inside the high pressure pump 1 is adjusted.
  • the late position 66 of the adjusting unit shown in FIG. 2 5 is characterized in that the axis of the bore of the rotary bearing 7 for Axis of the roller ring of the high pressure pump 1 are spaced apart by an offset 67.
  • the Injection adjuster piston 6 further comprises a recess 9 in which a pivoting movement of the lever element 8 accommodated in the pivot bearing 7 is also possible first inlet bore 10 and a second inlet bore angled to this 11.
  • a control slide bore is symmetrical to the central axis of the injection adjuster piston 6 13 added, in which a control slide 12 adjustable in the axial direction is stored.
  • the control slide 12 comprises a first channel 14 and one with this in Connected second channel 15. Furthermore, the one facing the cavity 24 A support ring 20 is added to the end face of the control slide 12.
  • the rotation of the Control slide 12 is by means of a disc-shaped element designed as a slot 16 ensures, which in the region of a recess 19 on the second end face 18th of the injection adjuster piston 6.
  • the slotted legs of the disc-shaped Element 16 engage in recesses on the outer peripheral surface of the control slide 12 are formed.
  • an intermediate plate 77 on which an annular stop surface 79 is formed becomes a stop for the second end face 18 of the injection adjuster piston 6 of the adjustment unit 5 shown for shifting the injection timing.
  • the intermediate plate 77 forms a stop surface for the first spring element 25, which has a first annular shape configured stop surface 52 on the inside 26 of the cold start acceleration piston 23 forms.
  • the first spring element 25, which is preferably designed as a coil spring is the intermediate plate 77 in contact with the housing 2 of the high pressure pump 1 and in System held on the adjusting unit 5 for shifting the injection timing.
  • the Cavity 24 which is essentially from the inside 26 of the cold start acceleration piston 23, the intermediate plate 77 and the second end face 18 of the injection adjuster piston 6 formed, also runs a further spring element 62, which is different from the second end face 18 of the injection adjuster piston 6 to the second contact face 53 on the Extends inside 26 of the cold start acceleration piston 23 and the injection adjuster piston 6 acted upon directly.
  • the slit-shaped, the axial movement of the control slide 12 limiting element 16 always in contact held on the second end face 18 of the injection adjuster piston 6.
  • a first end face 56 of a carrier element 55 bears against a third contact surface 54 on the inside 26 of the cold start acceleration piston 23.
  • the carrier element 55 comprises an axis 59 extending from the first end face 56 parallel to the axis of symmetry of the injection piston 6.
  • a stop is formed on this axis 59, which defines the maximum axial displacement of a spring support ring 57.
  • the spring support ring 57 essentially designed as a cylindrical component, comprises a first end face 57.1 and a second end face 58.
  • a first spring element 60 of a spring assembly 60 extends between a disk-shaped element 21 assigned to the first end face 56 and the first end face 57.1 of the spring support ring 57. 61.
  • the second spring element of the spring assembly 60, 61 extends between the second end face 58 of the spring support ring 57 and the support ring 20 of the control slide 12.
  • the first spring element 60 or the second spring element 61 accommodated within the installation space A (see FIG. 1), are connected in series to one another, the position of the spring support ring 57 depending on the resulting force exerted by the first spring element 60 of the spring stiffness c 2 and the second spring element 61 with spring stiffness c 1 on the spring support ring 57.
  • the spring support ring 57 is also provided with openings 63, through which, when the spring support ring 57 is in contact with the end face of the support disk 20 of the control slide 12, fuel flowing into the interior of the spring support ring 57 flows from the second channel 15 into the cavity 24 and fills it gradually, ie leads to a build-up of pressure in this.
  • the injection adjuster piston 6 is in the direction of an early start of injection Comparison to the illustration according to FIG. 2 in a stop ring 79 of the intermediate plate 77 employed state.
  • the first end face 17 of the injection adjuster piston is in this state 6 spaced from the housing side wall, whereas the control slide 12 from its control slide bore 13 in the interior of the injection adjuster piston 6 is extended.
  • the offset 67 shown in Figure 2 between the center of the Rotary bearing 7, the injection adjuster piston 6 and the pivot point of the unspecified Component of high-pressure pump 1 has dropped out, i.e. these pivot points lie on a vertical.
  • the control slide 12 is designed as a control slide and is determined by the suction chamber pressure, which is present through the opening 9, in equilibrium with the trailing piston springs brought and thus controls the position of the injection adjuster piston 6.
  • the spring support ring 57 is displaced on the axis 59 of the carrier 55 by the support disk 20 provided on its end face until an equilibrium of forces has been established within the spring assembly 60 or 61 and a further displacement of the spring support ring 57 begins the axis 59 of the carrier 55 is omitted.
  • the early position 65 of the injection adjuster piston 6 is that of the end face 27 of the cold start acceleration piston 23 assigned pressure chamber 28 relieved of pressure.
  • Via one of the adjustment units 5 for moving the start of injection assigned actuator in the form of a Electromagnet 41 can establish a fluid connection between an inlet 51 to actuator 41 and a pressure chamber bore 50 opening into its valve chamber is interrupted or be released.
  • the pressure chamber 28 is analogous to the representation according to FIG without pressure; i.e. the actuator 41 in the form of a solenoid valve closes the inlet 51 from the high pressure pump 1.
  • Figure 4 shows the actuator for shifting the injection timing in the steady state the high pressure pump with the injection adjuster piston in the late position.
  • the inlet 51 to the actuator is in shape of a solenoid valve 41 is released by the actuator and by the solenoid valve 41 associated valve chamber fuel via the pressure chamber bore 50 in the Pressure chamber 28 shoots. Due to the gradual increase in pressure in the pressure chamber 28 the end face 27 of the cold-start acceleration piston 23 is acted on such that it moves with its inside 26 towards the intermediate plate 77, one of which is annular extending stop surface 79 is formed.
  • the carrier 55 receiving the spring support ring 57 is displaced. Its first end face 56 bears against the third contact surface 54 on the bottom on the inside 26 of the cold start acceleration piston 23.
  • the carrier 55 with the spring support ring 57 which is displaceably received thereon and is acted upon by the first spring element with spring stiffness c 2 , moves in the direction of the support disk 20 of the control slide 12.
  • the inlet 51 from the housing 2 High pressure pump 1 is closed and the pressure chamber bore 50 is depressurized, due to the pressure build-up in the cavity 24, the cold start acceleration piston 23 in System to stop 29 on the wall of the adjustment unit 5.
  • Figure 5 shows a schematic representation of a side view of the high pressure pump.
  • the drive side of the high pressure pump is marked, on which in schematic representation of a pulley 4 is formed, which does not have a here Belt drive shown initiates the drive in the high pressure pump.
  • An adjustment unit 5 is flanged to the side of the housing 2 of the high-pressure pump 1, which serves to shift the start of injection.
  • reference numeral 74 are the flange screws characterized, with which the adjusting unit 5 on the housing 2 of the high pressure pump 1 is flanged.
  • the adjustment unit 5 stands with the housing 2 of the high-pressure pump via a first connecting pipe 72 connected.
  • the first connecting pipe 72 is connected to a hollow screw 70 Sealing elements 71 attached to the housing 2 of the high pressure pump 1 and with a Another hollow screw 70 in the region of the cold start acceleration piston 23 of the adjustment unit 5 connected to postpone the start of injection.
  • the further banjo bolt 70 are also analogous to the first banjo bolt 70 flat sealing rings 71 assigned.
  • a second connection pipe 73 extends from the adjustment unit 5 for shifting the injection timing to the housing 2 of the high-pressure pump 1, which is connected pressure-tight at the same time by means of banjo bolts 70.
  • Figure 5.1 shows a partial longitudinal section through the adjustment unit for shifting the start of injection with cold start acceleration pistons.
  • a connecting thread 75 for a hollow screw 70 is provided in the housing of the adjusting unit 5.
  • an annular groove 38 is provided on the lateral surface of the cold start acceleration piston 23, which is connected to the cavity 24 delimited by the cold start acceleration piston 23 and the injection adjuster piston 6 via a drain hole 39.
  • the end face 27 of the cold start acceleration piston 23 bears against the stop 29 on the housing side.
  • the inside 26 of the cold start acceleration piston 23 is designed such that a plurality of stop faces 52 and 53 are formed on the inside of the cold start acceleration piston 23, against which the first spring element 25 and the first end face 56 of a carrier 55 rest.
  • the first end face 56 of the carrier as shown in FIG. 5.2 serves to support the further spring element 62, which acts directly on the first end face 18 of the injection adjuster piston 6.
  • a spring support ring 57 is mounted on the axis 59 of the carrier 55, the first side 57.1 of which serves as a stop surface for the first spring element 60, designed with spring stiffness c 2 .
  • the second stop surface 53 of the spring support ring 57 supports the second spring element 61 of the spring assembly 60 or 61, wherein the second spring element is designed with a spring stiffness c 1 and acts on the support disk 20 of a control slide 12, not shown here.
  • FIG. 5.2 is a longitudinal section through the adjustment unit for displacement the start of injection with a coupling spring package between the cold start acceleration pistons and injection adjuster pistons.
  • the first spring element 25 bears on the first bearing surface 52, while the second bearing surface 53 and the third bearing surface 54 are combined in a stop surface for the first end face 56 of the spring carrier 55 as shown in FIGS. 2, 3 and 4.
  • a spring support ring 57 is slidably received on the axis 59 with a stop extending from the first end face 56 of the carrier 55.
  • the first side 57.1 of the spring support ring 57 is acted upon by the first spring element 60, designed in spring stiffness c 1 , while a second spring element 61, designed in spring stiffness c 1 , extends from the second side 58 of the spring support ring 57 to the support disk 20 of the control slide 12.
  • the control slide 12 is displaceably guided in a control slide bore 13 within the injection adjuster piston 6.
  • the injection adjuster piston 6 comprises, analogously to the representations according to FIGS. 2, 3 and 4, a rotary bearing 7, in which a lever shoulder 8 indicated here for adjusting an actuating element projects on a high-pressure pump 1 not shown in FIG. 5.3. In order to enable a pivoting movement of the lever shoulder 8 when the injection adjuster piston 6 is axially displaced, there is an elongate recess 9 above the pivot bearing 7.
  • the injection adjuster piston 6 is traversed by a first inlet bore 10, which opens into an inlet bore 11 running at an angle to this. Via the second inlet bore 11, the first channel 14 in the control slide 12 can be pressurized, which is connected to a second channel 15.
  • the second channel 15 of the control slide 12 opens in the region of the end face of a support disk 20, on which the second spring element 61, designed with spring stiffness c 1 , is supported.
  • the stop surface 79 forms the system for the second end face 17 of the injection adjuster piston 6, reference numeral 78 denotes a sealing plate.
  • the cold start acceleration piston 23 is analogous to the design variants according to FIGS Representations in Figures 2, 3 and 4 acted upon by a first spring element 25.
  • the the second end face of the injection adjuster piston 6 directly acting further spring 62 (the further spring element 62) is supported on the first end face 56 of the in FIG. 5.3 in modified embodiment shown carrier 55 from.
  • annular groove 38 is a hollow screw connection 70 or 75 assigned, via which by means of the first connecting pipe 72 (see illustration according to FIG. 5), an outflow of unnecessary fuel into the Housing 2 of the high pressure pump 1 can take place.
  • the position of the injection adjuster piston is shown in FIG. 5.2 when the internal combustion engine stands, but the solenoid valve 41 is energized. In this state the internal combustion engine when the engine is about to start warm.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
EP02022594A 2001-11-21 2002-10-09 Pompe à injection distributrice mécanique à accélération de démarrage à froid Expired - Lifetime EP1314873B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10156989A DE10156989A1 (de) 2001-11-21 2001-11-21 Mechanische Verteilereinspritzpumpe mit Kaltstartbeschleunigung
DE10156989 2001-11-21

Publications (3)

Publication Number Publication Date
EP1314873A2 true EP1314873A2 (fr) 2003-05-28
EP1314873A3 EP1314873A3 (fr) 2005-05-18
EP1314873B1 EP1314873B1 (fr) 2008-08-06

Family

ID=7706380

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02022594A Expired - Lifetime EP1314873B1 (fr) 2001-11-21 2002-10-09 Pompe à injection distributrice mécanique à accélération de démarrage à froid

Country Status (3)

Country Link
US (1) US6748930B2 (fr)
EP (1) EP1314873B1 (fr)
DE (2) DE10156989A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3985234B2 (ja) * 2004-06-29 2007-10-03 ソニー株式会社 音像定位装置
EP1835168B1 (fr) * 2006-03-17 2008-12-03 Delphi Technologies, Inc. Pompe de carburant
US7751907B2 (en) 2007-05-24 2010-07-06 Smiths Medical Asd, Inc. Expert system for insulin pump therapy
US8986253B2 (en) 2008-01-25 2015-03-24 Tandem Diabetes Care, Inc. Two chamber pumps and related methods
US8408421B2 (en) 2008-09-16 2013-04-02 Tandem Diabetes Care, Inc. Flow regulating stopcocks and related methods
WO2010033878A2 (fr) 2008-09-19 2010-03-25 David Brown Dispositif de mesure de la concentration d’un soluté et procédés associés
EP3284494A1 (fr) 2009-07-30 2018-02-21 Tandem Diabetes Care, Inc. Système de pompe à perfusion portable
US9180242B2 (en) 2012-05-17 2015-11-10 Tandem Diabetes Care, Inc. Methods and devices for multiple fluid transfer
US9173998B2 (en) 2013-03-14 2015-11-03 Tandem Diabetes Care, Inc. System and method for detecting occlusions in an infusion pump

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4408591A (en) * 1980-11-15 1983-10-11 Diesel Kiki Co., Ltd. Injection timing control device for distributor-type fuel injection pumps
US4610234A (en) * 1984-06-12 1986-09-09 Diesel Kiki Co., Ltd. Injection timing control device for distributor-type fuel injection pumps

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2839014A1 (de) * 1978-09-07 1980-03-20 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
GB2068590B (en) * 1980-01-22 1983-06-22 Lucas Industries Ltd Fuel pumping apparatus
DE3517974A1 (de) * 1985-05-18 1986-11-20 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3822257A1 (de) * 1988-07-01 1990-01-04 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3943246A1 (de) * 1989-12-29 1991-07-04 Bosch Gmbh Robert Kraftstoffeinspritzpumpe

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4408591A (en) * 1980-11-15 1983-10-11 Diesel Kiki Co., Ltd. Injection timing control device for distributor-type fuel injection pumps
US4610234A (en) * 1984-06-12 1986-09-09 Diesel Kiki Co., Ltd. Injection timing control device for distributor-type fuel injection pumps

Also Published As

Publication number Publication date
DE50212596D1 (de) 2008-09-18
EP1314873B1 (fr) 2008-08-06
US6748930B2 (en) 2004-06-15
US20030121504A1 (en) 2003-07-03
DE10156989A1 (de) 2003-06-05
EP1314873A3 (fr) 2005-05-18

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