EP1314873B1 - 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
EP1314873B1
EP1314873B1 EP02022594A EP02022594A EP1314873B1 EP 1314873 B1 EP1314873 B1 EP 1314873B1 EP 02022594 A EP02022594 A EP 02022594A EP 02022594 A EP02022594 A EP 02022594A EP 1314873 B1 EP1314873 B1 EP 1314873B1
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EP
European Patent Office
Prior art keywords
spring
piston
pressure pump
face
injection
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
EP02022594A
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German (de)
English (en)
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EP1314873A2 (fr
EP1314873A3 (fr
Inventor
Guenter Bofinger
David Banham
Volker Freudl
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Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Publication date
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Publication of EP1314873A2 publication Critical patent/EP1314873A2/fr
Publication of EP1314873A3 publication Critical patent/EP1314873A3/fr
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Publication of EP1314873B1 publication Critical patent/EP1314873B1/fr
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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 due to constantly increasing requirements due to stricter exhaust gas regulations for gasoline engines and for self-igniting internal combustion engines, the start of injection, especially in self-igniting internal combustion engines, to adapt to the respective operating phase of the internal combustion engine.
  • the cold running phase in particular at low outside temperatures, it is necessary to adjust the start of injection to earlier on diesel distributor injection pumps and thereby achieve a lower emission and noise emission with regard to particle emission and an emission-free cold running phase that follows.
  • With increasing speeds of the internal combustion engine it is necessary to advance the start of delivery of the injection pump to compensate for the time lag caused by injection and ignition delay.
  • diesel fuel takes a certain period of time to change from the liquid state to the gaseous state and, in this state, to form a flammable, high-pressure, self-igniting mixture with the combustion air.
  • the time required between the beginning of the injection and the start of combustion is referred to as ignition delay in self-igniting internal combustion engines. This is 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 injection nozzle of the fuel injector.
  • the ignition delay in self-igniting internal combustion engines is usually of the order of 1 to 2 ms. During the cold-running phase at low outside temperatures, this period of time increases, which leads to the formation of soot by unburned fuel, which passes through the exhaust system in the environment.
  • a hydraulic measure for the start acceleration is a temporary increase in the interior pressure of the distributor injection pump during the cold start and the immediate at this subsequent cold-running phase of the self-igniting internal combustion engine.
  • the disadvantage of this measure is a late release of the injection adjusting piston due to the slowly building pressure in the interior of the distributor injection pump.
  • Another way to adjust the start of injection to early is to move by rotating a designed as a roller ring component during start and the cold running phase of the self-igniting internal combustion engine Einspritzverstellerkolben and thus the start of injection to early.
  • Another measure that can be carried out by mechanical means for cold-start acceleration is to press on one side of the injection adjusting piston by means of an eccentric shaft and thereby displace the injection adjusting piston in such a way that the start of injection shifts early (see, for example, US Pat U.S.-A-4,408,591 ).
  • two spring elements different spring stiffness 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, with the spring stiffness responsible for the cold start, while the spring stiffness c 2 of the remaining spring element is designed with respect to the normal operation.
  • the spring piston of the Fedemvers acting on the injection plunger is biased while the cold-start acceleration piston associated spring element is in an untensioned position.
  • a stepped arrangement of a plurality of contact surfaces can be formed on the inside of the Kaltstartbeuggungskolbens, wherein the individual contact surfaces are preferably designed to run as annular surfaces.
  • FIG. 1 shows a high-pressure pump with Tecverstelltechnik, as known from the prior art.
  • the high-pressure pump 1 comprises a housing 2, on the underside of which an adjustment unit 5 is flanged to shift the start of injection.
  • the adjustment unit 5 for shifting the injection time comprises a two-part housing, wherein on a housing structure 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 timing comprises a displaceably mounted Einspritzverstellerkolben 6.
  • a rotary bearing 7 is arranged, which for receiving a in FIG. 1 not shown levers is used.
  • a roller ring of a high-pressure pump 1, not shown here can be adjusted within the housing 2 such that the start of injection of fuel is shifted into the combustion chambers of an internal combustion engine.
  • This lever is also referred to as adjusting a sprue piston for adjusting the roller ring.
  • the lever received in the rotary bearing 7 of the injection adjusting piston 6 passes through an opening 9 in the injection adjusting piston, which is dimensioned such that a pivoting movement of the lever of the rotary bearing 7 within the injection adjusting piston 6 is possible.
  • the Einspritzverstellerkolben 6 is of a first, extending substantially in the vertical direction first inlet bore 10 and a substantially perpendicular to this second inlet bore 11 through.
  • the second inlet bore 11 opens into a control slide bore 13, which runs substantially parallel to the axis of symmetry of the injection adjusting piston 6.
  • a piston-shaped control slide 12 is inserted, which is provided at its a cavity 24 facing end face with an enlarged diameter exit hole.
  • the control slide 12 corresponds to a control piston and is referred to in combination with the Einspritzverstellerkolben 6 as a follower or Servospritzverstellerkolben. There is a connection between a first channel 14 running transversely to the axis of symmetry of the control slide 12 and a second channel 15 running in the control slide 12, the second passage 15 opening into the region of the control slide 12, which is formed in an enlarged inner diameter.
  • the control slide 12 is associated with a slotted disc 16 on its outer peripheral surface, which determines the axial displacement of the control slide 12 within the Einspritzverstellerkolbens 6, the slotted disc forms a stop 22 for the control slide 12th
  • the slotted disc 16 is located within a recess 19 of the Einspritzverstellerkolbens 6 at the second end face 18 of the Einspritzverstellerkolbens 6, while the first end face 17 of the Einspritzverstellerkolbens 6 in.
  • FIG. 1 shown state of a housing boundary wall of the adjusting unit 5 assigns to shift the injection timing.
  • the control slide 12 comprises a support disk 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 supported on an intermediate plate 30 on the side opposite the inside 26.
  • an annular projection is formed, which serves as a stop surface for the second end face 18 of the Einspritzverstellerkolbens 6.
  • a follower piston / control slide retaining spring 32 is inserted between the first spring element 25 and the control spring 31.
  • the sleeve body 34 whose lateral surface comprises individual openings 35, has a first sleeve body stop 36 and a second sleeve body stop 37.
  • the control slide / follower 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 region of the second end face 18 of the Einspritzverstellerkolbens 6.
  • the cold-start acceleration piston 23 shown here is braced, with its end face 27 facing a pressure chamber 28, against a stop 29 formed on the housing wall of the adjusting unit 5.
  • an annular groove 38 is inserted, which communicates via a drain hole 39 with the cavity 24, from the inside 26 of the cold start acceleration piston 23, the intermediate plate 30 and the second end face 18 of the injection adjusting piston 6 in the region of the recess 19th is limited.
  • a disadvantage of this embodiment of a high-pressure pump 1 for supplying a fuel injection system with fuel is the fact that there is a gap 33 between the inside 26 of the cold start acceleration piston 23 and the first sleeve body stop 36.
  • This gap 33 causes that upon 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 executed therein an uncontrolled movement of the Einspritzverstellerkolbens 6 can occur .
  • For a stable adjustment in the lower speed range of the high-pressure pump 1 is difficult to achieve, since between the first sleeve body stop 36 and the opposite portion of the inner side 26 of the cold start acceleration piston 23 remains a design-related clearance. Since the second sleeve body stop 37 engages over the support disk 20 of the control slide 12, the position of the first sleeve body stop 36 of the sleeve body 34 is fixed, resulting in the formation of the annular gap 33.
  • FIG. 2 shows an adjusting unit for shifting the start of injection in longitudinal section.
  • Analogous to the representation according to FIG. 1 is the housing 2 of a high-pressure pump 1 associated with an adjustment unit 5 for shifting the injection timing.
  • an Einspritzverstellerkolben 6 is added, which comprises a pivot bearing 7, in which a not shown here lever member 8 is received, which adjusts a roller ring within the high-pressure pump 1.
  • FIG. 2 illustrated late position 66 of the adjusting unit 5 is characterized in that the axis of the bore of the pivot bearing 7 to the axis of the roller ring of the high-pressure pump 1 by an offset 67 apart.
  • the Einspritzverstellerkolben 6 further comprises a recess 9 in which a pivotal movement of the lever member 8 received in the pivot bearing 7 is possible, further comprises a first inlet bore 10 and a second, angled thereto extending inlet bore 11. Symmetrically to the central axis of the Einspritzverstellerkolbens 6 a control spool bore 13 is added in which a control slide 12 is mounted adjustably in the axial direction.
  • the control slide 12 comprises a first channel 14 and a second channel 15 communicating therewith End face of the control slide 12 a support ring 20 added.
  • the rotational movement of the control slide 12 is ensured by means of a disk-shaped element 16 designed as a slot, which rests in the region of a recess 19 on the second end face 18 of the injection adjusting piston 6.
  • the slotted legs of the disc-shaped element 16 engage in recesses which are formed on the outer peripheral surface of the control slide 12.
  • an intermediate plate 77 on which an annular stop surface 79 is formed, a stop for the second end face 18 of the Einspritzverstellerkolbens 6 of the adjusting unit 5 is shown for shifting the injection timing.
  • the intermediate plate 77 forms a stop surface for the first spring element 25, which forms a first annularly configured stop surface 52 on the inner side 26 of the cold start acceleration piston 23.
  • the first spring element 25 which is preferably designed as a helical spring, the intermediate plate 77 is held in contact with the housing 2 of the high-pressure pump 1 and in contact with the adjusting unit 5 for shifting the injection time.
  • a further spring element 62 which extends from the second end face 18 of the Einspritzverstellerkolbens 6 to the second bearing surface 53 runs extends on the inside 26 of the cold start acceleration piston 23 and the injection adjusting piston 6 is applied directly.
  • a first end face 56 of a carrier element 55 abuts.
  • the support member 55 includes an extending from the first end face 56 parallel to the axis of symmetry of the Einspritzver actuator piston 6 axis 59.
  • a stop is formed, which determines the maximum axial displacement of a spring support ring 57.
  • the spring support ring 57 formed substantially as a cylindrical member, comprises a first end face 57.1 and a second end face 58. Between a first end face 56 associated disk-shaped element 21 and the first end face 57.1 of the spring support ring 57, a first spring element 60 of a spring assembly 60 extends, 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 and the second spring element 61 received within the installation space A (see. FIG. 1 ), are connected in series with each other, wherein the position of the spring support ring 57 depends on the resultant 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, via which flows when the spring support ring 57 on the end face of the support plate 20 of the control slide 12 into the interior of the spring support ring 57 inflowing fuel from the second channel 15 into the cavity 24 and gradually filled, ie to a Pressure build-up in this leads.
  • FIG. 3 is the adjustment according to FIG. 2 reproduced with an adjusting unit for shifting the injection timing, the Einspritzverstellerkolben is put into spring.
  • the Einspritzverstellerkolben 6 is compared to the representation according to FIG. 2 in a salaried to the stop ring 79 of the intermediate plate 77 state.
  • the first end face 17 of the Einspritzverstellerkolbens 6 is spaced from the housing-side wall, whereas the control slide 12 is extended from its control spool bore 13 in the interior of the Einspritzverstellerkolbens 6.
  • the second inlet bore 11 and the first channel 14 which passes through the control slide 12 perpendicular to the first axis of symmetry, prevented.
  • the in FIG. 2 shown offset 67 between the center of the pivot bearing 7, the Einspritzverstellerkolbens 6 and the pivot point of the unspecified component of the high-pressure pump 1 has dropped, ie these fulcrums are on a vertical.
  • the control slide 12 is designed as a control slide and is brought by the Saugraumtik, which is present through the opening 9, in equilibrium with the follower piston springs and thus controls the position of the Einspritzverstellerkolbens. 6
  • FIG. 3 shows that in this operating state of the adjusting unit 5 to move the injection start of the support ring 57 and the support plate 20 of the control slide 12 in abutment with each other.
  • the between the second end face 58 of the spring support ring 57 and the corresponding contact surface of the support plate 20 of the Control slide 12 recessed second spring element with spring stiffness c 1 is compressed accordingly.
  • the first spring element 60 with spring stiffness c 2 of the spring assembly 60 or 61 remains essentially in its already in FIG. 2 shown location.
  • 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 the axis 59 of the carrier 55 is omitted.
  • FIG. 4 shows the adjusting unit for shifting the injection timing in the stationary state of the high-pressure pump with injection valve set in late position.
  • the first spring element 25 is compressed.
  • the contact surface 53 during axial movement of the cold-start acceleration piston 23 in the direction of the second end face 18 of the Einspritzverstellerkolbens 6 is moved.
  • the biasing force generated by the further spring element 62 increases, that is, the Einspritzverstellerkolben of his in FIG. 3 shown spring day 65 in his in FIG. 4 shown late position 66.
  • the first inlet bore 10 and the second inlet bore 11 are in connection with the first channel 14 and thus the second channel 15 of the control slide 12 when starting the internal combustion engine.
  • fuel flows into the cavity 24 via the bores or channels and the opening 63 in the spring support ring 57.
  • the solenoid valve 41 the inlet 51 from the housing 2 of the high-pressure pump 1 and thus the pressure chamber bore 50 is depressurized, driven by the pressure build-up in the cavity 24, the cold start acceleration piston 23 in abutment against the stop 29 on the wall of the adjustment unit 5.
  • FIG. 5 shows a schematic representation of a side view of the high-pressure pump.
  • a housing 2 of a high-pressure pump 1 for supplying an internal combustion engine with fuel under high pressure is reproduced.
  • Reference numeral 3 denotes the drive side of the high-pressure pump, on which a pulley 4 is formed in a schematic representation, which introduces the drive into the high-pressure pump via a belt drive (not shown here).
  • an adjusting unit 5 is flanged, which serves to shift the start of injection.
  • the flange screws are marked, with which the adjusting unit 5 is flanged to the housing 2 of the high-pressure pump 1.
  • the adjusting unit 5 communicates with the housing 2 of the high pressure pump via a first connecting pipe 72 in connection.
  • the first connecting pipe 72 is fastened to a hollow screw 70 with sealing elements 71 on the housing 2 of the high-pressure pump 1 and connected to a further hollow screw 70 in the region of the cold-start acceleration piston 23 of the adjusting unit 5 for shifting the start of injection.
  • the further hollow screw 70 are also analogous to the first-mentioned hollow screw 70 flat sealing rings 71 assigned.
  • a second connecting pipe 73 extends from the adjusting unit 5 for shifting the injection time to the housing 2 of the high-pressure pump 1, which is simultaneously pressure-tightly connected by means of hollow screws 70.
  • Figure 5.1 shows a partial longitudinal section through the adjusting unit for shifting the start of injection with cold start acceleration piston.
  • the first end face 56 of the carrier as shown in FIG Figure 5.2 serves in addition to the support of the first spring element 60 for supporting the further spring element 62, which the first end face 18 of the Einspritzverstellerkolbens 6 applied directly.
  • a spring support ring 57 is mounted, the first side 57.1 serves as a stop surface for the first spring element 60, executed in 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 and 61, wherein the second spring element is formed in a spring stiffness c 1 and the support plate 20 of a control slide 12, not shown here applied.
  • the representation according to Figure 5.2 is a longitudinal section through the adjustment to move the start of injection with a coupling spring package between the cold start acceleration piston and Einspritzverstellerkolben refer.
  • the first side 57.1 of the spring support ring 57 is acted upon by the first spring element 60, executed in spring stiffness c 1 , while extending from the second side 58 of the spring support ring 57, a second spring element 61, executed in spring stiffness c 1 , the support plate 20 of the control slide 12.
  • the control slide 12 is slidably guided within the Einspritzverstellerkolbens 6 in a control slide bore 13.
  • the Einspritzverstellerkolben 6 includes analogous to the illustrations according to the Figures 2 .
  • a pivot bearing 7 in which a lever attachment 8 indicated here for the purpose of adjusting an actuating element protrudes on a high-pressure pump 1 (not shown in FIG. 5.3).
  • a lever attachment 8 indicated here for the purpose of adjusting an actuating element protrudes on a high-pressure pump 1 (not shown in FIG. 5.3).
  • an elongated recess 9 is located above the pivot bearing 7.
  • the Einspritzverstellerkolben 6 is traversed by a first inlet bore 10, which opens in an angularly extending to this inlet bore 11. Via the second inlet bore 11, the first channel 14 in the control slide 12 can be pressurized, which is in communication with a second channel 15.
  • the second channel 15 of the control slide 12 opens in the region of the end face of a support plate 20, on which the second spring element 61, executed in spring stiffness c 1 , is supported.
  • an intermediate plate 77 Between the housing 5 of the adjusting unit and a housing 2 of the high-pressure pump 1, which is only indicated here, there is an intermediate plate 77, on which an annular stop surface 79 extends is trained.
  • the abutment surface 79 forms the abutment for the second end face 17 of the Einspritzverstellerkolbens 6, reference numeral 78 denotes a sealing plate.
  • the cold-start acceleration piston 23 is analogous to the variants according to the illustrations in FIG. 2 . 3 and 4 acted upon by a first spring element 25.
  • the further spring 62 (the further spring element 62) acting directly on the second end face of the injection adjusting piston 6 is supported on the first end face 56 of the carrier 55 shown in modified form in FIG. 5.3.

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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)

Claims (12)

  1. Pompe haute pression pour l'alimentation des moteurs à combustion interne avec du carburant et dont le boîtier (2) comporte une unité de réglage (5) pour déplacer le point d'injection, cette unité comprenant un piston de réglage d'injection (6) avec des perçage d'alimentation (10, 11) et un tiroir de réglage (12) est logé de manière mobile dans le piston de réglage d'injection (6), ce tiroir étant sollicité par une force de précontrainte appliquée sur sa face frontale (18) tournée vers le piston d'accélération de démarrage à froid (23),
    caractérisée en ce qu'
    entre le piston d'accélération de démarrage à froid (23) et une face frontale (18) du piston de réglage d'injection (6), il est prévu un élément de ressort (62) sollicitant directement la butée (22) du piston de réglage d'injection (6) ainsi qu'un paquet de ressorts (60, 61) indépendant de cet élément de ressort, prévu sur un support (55) et agissant sur le tiroir de réglage (12).
  2. Pompe haute pression selon la revendication 1,
    caractérisée en ce que
    les éléments de ressort du paquet de ressorts (60, 61) sont branchés en série.
  3. Pompe haute pression selon la revendication 1,
    caractérisée en ce que
    le premier élément de ressort (60) et le second élément de ressort (61) du paquet de ressorts (60, 61) s'appuient contre une bague d'appui de ressort (57) logée de manière mobile sur un support (55).
  4. Pompe haute pression selon la revendication 3,
    caractérisée en ce que
    la bague d'appui de ressort (57) comprend une première face frontale (57.1) et une seconde face frontale (58).
  5. Pompe haute pression selon la revendication 3,
    caractérisée en ce que
    le premier élément de ressort (60) du paquet de ressorts (60, 61) est logé entre le piston d'accélération de démarrage à froid (23) et la bague d'appui de ressort (57) et présente une première rigidité de ressort c1.
  6. Pompe haute pression selon la revendication 3,
    caractérisée en ce que
    le second élément de ressort (61) du paquet de ressorts (60, 61) est logé entre le piston de réglage d'injection (6) et la bague d'appui de ressort (57) et présente une seconde rigidité de ressort c1.
  7. Pompe haute pression selon la revendication 1,
    caractérisée en ce que
    le piston d'accélération de démarrage à froid (23) comporte plusieurs surfaces d'appui étagées (52, 53, 54) sur sa surface intérieure (26) tournée vers une cavité (24).
  8. Pompe haute pression selon la revendication 7,
    caractérisée par
    un premier élément de ressort (25) logé entre une première surface d'appui (52) du piston d'accélération de démarrage à froid (23) et une plaque intermédiaire (30, 77) formant une bague d'appui (79) pour le piston de réglage d'injection (6).
  9. Pompe haute pression selon la revendication 7,
    caractérisée en ce que
    l'élément de ressort (62) qui sollicite directement le piston de réglage d'injection (6) est appliqué contre la seconde surface d'appui (53) du piston d'accélération de démarrage à froid (23).
  10. Pompe haute pression selon la revendication 1,
    caractérisée en ce que
    l'élément de ressort (62) qui sollicite la seconde face frontale (18) du piston de réglage d'injection (6) applique contre celui-ci une rondelle fendue (16) dont les branches fendues pénètrent dans des cavités prévues pour limiter la course axiale du tiroir de réglage (12).
  11. Pompe haute pression selon la revendication 6,
    caractérisée en ce que
    le second élément de ressort (61) du paquet de ressorts (60, 61) est logé entre la bague d'appui de ressort (57) du support (55) et une bague d'appui (20) du tiroir de réglage (12).
  12. Pompe haute pression selon l'une des revendications précédentes,
    caractérisée en ce que
    le tiroir de réglage (12) comporte un second canal (15) traversant la rondelle d'appui (20) et qui, lorsque le tiroir de réglage (12) est appliqué contre la bague d'appui de ressort (57) remplit par les ouvertures (63) prévues sur la bague d'appui, la cavité (24) entre le piston d'accélération de démarrage à froid (23) et le piston de réglage d'injection (6) dans l'unité de réglage (5).
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)

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

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EP02022594A Expired - Lifetime EP1314873B1 (fr) 2001-11-21 2002-10-09 Pompe à injection distributrice mécanique à accélération de démarrage à froid

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

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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
US8650937B2 (en) 2008-09-19 2014-02-18 Tandem Diabetes Care, Inc. Solute concentration measurement device and related methods
AU2010278894B2 (en) 2009-07-30 2014-01-30 Tandem Diabetes Care, Inc. Infusion pump system with disposable cartridge having pressure venting and pressure feedback
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

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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
JPS5786533A (en) * 1980-11-15 1982-05-29 Diesel Kiki Co Ltd Regulating device of injection timing in distributor type fuel injection pump
JPS6141840U (ja) * 1984-06-12 1986-03-17 株式会社ボッシュオートモーティブ システム 分配型燃料噴射ポンプの噴射時期調整装置
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

Also Published As

Publication number Publication date
US20030121504A1 (en) 2003-07-03
EP1314873A2 (fr) 2003-05-28
US6748930B2 (en) 2004-06-15
DE50212596D1 (de) 2008-09-18
DE10156989A1 (de) 2003-06-05
EP1314873A3 (fr) 2005-05-18

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