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EP0597249A1 - Dispositif d'injection de combustible, in particulier pompe-injecteur pour moteurs à combustion interne - Google Patents

Dispositif d'injection de combustible, in particulier pompe-injecteur pour moteurs à combustion interne Download PDF

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Publication number
EP0597249A1
EP0597249A1 EP93116228A EP93116228A EP0597249A1 EP 0597249 A1 EP0597249 A1 EP 0597249A1 EP 93116228 A EP93116228 A EP 93116228A EP 93116228 A EP93116228 A EP 93116228A EP 0597249 A1 EP0597249 A1 EP 0597249A1
Authority
EP
European Patent Office
Prior art keywords
tappet
pin
fuel injection
injection device
pump
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
EP93116228A
Other languages
German (de)
English (en)
Other versions
EP0597249B1 (fr
Inventor
François Agrain
François Rossignol
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0597249A1 publication Critical patent/EP0597249A1/fr
Application granted granted Critical
Publication of EP0597249B1 publication Critical patent/EP0597249B1/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
    • 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
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • 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
    • F02M59/48—Assembling; Disassembling; Replacing

Definitions

  • the invention is based on a fuel injection device, in particular a pump nozzle for internal combustion engines, according to the preamble of claim 1.
  • a fuel injection device of this type known from DE-OS 39 43 419
  • a pump piston axially guided in a cylinder bore of a pump housing is driven back and forth by a cam drive.
  • the pump piston with its end facing away from the cam drive, delimits a pump working chamber in the cylinder bore into which a fuel line opens and which is connected via a pressure channel to an injection valve which projects into the combustion chamber of the internal combustion engine to be supplied.
  • Both the start of high-pressure delivery of the fuel in the pump work space and thus the start of injection and the amount of fuel to be injected are electrically controlled by the closing time of a solenoid valve arranged in the fuel supply line, depending on the operating parameters of the internal combustion engine to be supplied.
  • the transmission of the drive movement of the cam drive to the pump piston takes place via a tappet pin, which acts on the pump piston via a tappet insert.
  • the tappet insert is arranged in a guide sleeve which slides in a guide tube fixed to the housing and which transmits the restoring force of a spring to the pump piston which is clamped between the guide sleeve and the tappet insert via a coupling part.
  • the tappet pin with its end facing the pump piston is guided and secured in the tappet insert in a relatively complex manner, since the tappet pin is axially secured in the tappet insert in the known pump nozzle via a locking ring which is latched into the tappet and is in an axial position between the end face of the tappet insert and an intermediate sleeve is fixed, the intermediate sleeve in turn being held axially on the tappet pin via a snap ring in the bore of the guide sleeve which guides the tappet pin.
  • the fuel injection device according to the invention with the characterizing features of claim 1 has the advantage that by using an axial securing element with elastic properties, the tappet bolt can be installed or removed with the securing element inserted, without additional components and disassembly of the pump being necessary, which significantly reduces manufacturing and assembly costs.
  • both the connection between the tappet pin and the tappet insert, as well as according to claim 2 the connection between the tappet pin and the transmission member to the camshaft are designed in the manner of a ball joint and, according to claim 3, are advantageously axially secured via an elastic securing element.
  • This elastic deformability of the securing element not only simplifies the assembly of the tappet bolt but also protects the cam drive against mechanical destruction when the pump piston is blocked, since the transmission member is pulled out of the bearing in the tappet bolt in this case.
  • the elastic securing element is advantageously designed as an O-ring, which has both limited deformability and high thermal and mechanical strength.
  • the design of the groove guiding the ring is carried out with the required radial play in order to ensure that the ring can be easily expanded while the ball pin is being passed through chern. It is advantageously possible to set the force required for assembly or the independent emergency disengagement of the ball head, both by dimensioning the ring and the groove.
  • the embodiments of snap rings mentioned in claims 5 to 10 have the advantage that they are easy to obtain as commercially available components and at low cost, the use of circular spring wire further enhancing the elastic properties of these snap rings.
  • the design of the securing element according to claim 11 offers the advantage that an annular groove in the region of the ball socket can be dispensed with, which enables the component carrying it to be shortened.
  • FIG. 1 shows a longitudinal section through part of a pump nozzle, with a schematic representation of the functionally important components adjoining it, in which the position of the tappet piston and its connection to the adjacent components, as well as a first embodiment of its axial securing in the form of a circular snap ring is shown
  • 2 shows a second exemplary embodiment of the axial securing between the tappet bolt and a tappet insert connecting it to the pump piston, in which an O-ring is inserted into the bore of the tappet sleeve guiding the tappet insert
  • FIGS. 3 to 6 show further embodiment variants of the one in FIG.
  • Figure 7 shows an embodiment in which the axial securing of the connection between the tappet pin and a rocker pin driving this takes place via a locking ring which is guided in an annular groove of the tappet pin
  • Figure 8 a wide Res embodiment analogous to Figure 7, in which the axial securing between rocker arm pin and tappet pin via one or more molded sheet metal parts pushed onto the tappet pin.
  • a pump piston 1 is guided axially in a cylinder bore 3 of a pump housing 5 and delimits a pump work chamber 7 with its end face there. With its end facing away from the pump work chamber 7, the pump piston 1 projects into a plunger 9, which is connected to a rocker arm 11 of a cam drive, not shown, via which the pump piston 1 is moved axially back and forth.
  • the pump work chamber 7 is connected via a pressure line 13 to an injection valve 15 which projects into the combustion chamber of the internal combustion engine to be supplied and which is arranged in the pump housing 5 and which opens when the injection pressure in the pump work chamber 7 and the pressure line 13 reaches a certain injection pressure and after sinking closes below this injection pressure.
  • a fuel line 17 opens into it, which starts from a fuel reservoir 19 and in which a fuel feed pump 21 and a magnetically controlled changeover valve 23 are arranged.
  • the changeover valve 23 is controlled as a function of the operating parameters of the internal combustion engine and regulates the beginning and the end of the high-pressure delivery via its opening or closing.
  • the plunger assembly 9 driving the pump piston 1 consists of a plunger pin 25 which acts axially on the pump piston 1 via a cylindrical plunger insert 27 inserted into a plunger sleeve 35 and which is actuated by the rocker arm 11 on its end face remote from the plunger insert 27.
  • the pump piston 1 has, at its end facing away from the pump working space 7, a head piece 31, which is formed by a ring recess 29 and projects into the plunger sleeve 35, with which it projects into a bore 33 in the plunger insert 27 and with its end face it bears against the plunger insert 27.
  • the plunger insert 27 is guided in the plunger sleeve 35, which in turn is axially slidably guided in a bore 37 of a pipe socket 38 of the pump housing 5 that runs coaxially to the cylinder bore 3 and that has an inwardly angled area 39 on its end face facing the pump piston 1, which has one Blind hole with passage opening for the head piece 31 forms.
  • the tappet sleeve 35 has an eccentric bore 47 in the angled region 39 through which the head 31 of the pump piston 1 is threaded into the tappet sleeve 35 during the preassembly of the tappet 9 and then through the Boh tion 33 of the plunger insert 27 is fixed in the middle and thus in contact with the angled area 39.
  • the tappet sleeve 35 has an elongated hole 49 in which a ball 51, which is guided in an annular groove 53 in the bore 37, is arranged.
  • the tappet sleeve 35 widens to form a flange 41 on which a return spring 43 engages, which surrounds the tappet sleeve 35 and the pipe socket 38 and, on the other hand, is supported on a housing shoulder 45 of the pump housing 5.
  • the restoring spring 43 thus counteracts the tappet movement in the direction of the pump working space 7 via the tappet sleeve 35 and brings the pump piston 1 coupled to the tappet sleeve 35 into its initial position during its suction stroke and returning tappet 9, i.e. top dead center.
  • the plunger pin 25 has on its side facing the pump piston 1 a spherical head 55 with a partial spherical surface facing away from the pump piston 1 and ending at the stem of the plunger pin 25, with the end face of which it is formed in a ball joint-like manner over an angular range of a maximum of 180 in one on the end face of the plunger insert 27 Ball socket 57 is mounted.
  • Axial securing of the tappet pin 25 against slipping out in the unloaded, unpressurized state at the end of the pump piston outward movement takes place in this exemplary embodiment via a circular locking ring 59, which is mounted on the side of the ball head 55 facing away from the tappet insert 27 in an annular groove 61 in the bore 37 that he can widen when pulling out the tappet pin 25 with a certain force to the extent of the outer diameter of the ball head 55.
  • the plunger pin 25 has a ball socket 63 in which a ball head 65 of a rocker arm pin 67 screwed vertically into the rocker arm 11 and similar to the ball head 55 with a larger ball diameter than the shaft is mounted.
  • the ball head 63 of the rocker arm pin 67 is also axially secured by means of a circular elastic locking ring 59 which engages behind the ball head 65 via a flanged sheet metal sleeve 69 which was pushed onto the rocker arm pin 67 on the rocker arm pin 67 before the rocker arm pin 67 was installed, and so in Holds on the ball socket 63, the sheet metal sleeve 69 is axially secured via a plurality of pronounced spring tongues 73 distributed over the circumference, which engage in a groove 75 on the outer circumference of the ball socket 63.
  • the exemplary embodiment shown in FIG. 2 differs from that of FIG. 1 only in the type of axial securing of the tappet pin 25 in the bore 37 of the tappet sleeve 35.
  • the securing element is here a 0-ring 77 with elastic properties (eg Vitton ring ) formed, which is guided in a semicircular or rectangular annular groove 61 in cross section that it can expand under a certain force to the size of the outer diameter of the ball head 55, so that a simple assembly of the plunger pin 25 in the plunger insert 27 is possible.
  • FIGS. 3 to 6 show different exemplary embodiments of the locking rings 59, this in FIG. 3 being an open wire spring ring which is curved in the form of a 5-surface closed polygon train, the outer diameter D1 of which is equal to the basic groove diameter and the inner diameter D2 is smaller than the outer diameter of the ball head 55, 65 is.
  • the assembly or disassembly force of the tappet pin 25 can be changed via the wire stiffness of the circular wire.
  • the leg is shortened at the gap b, in order to avoid an overlap of the legs during assembly and, in connection with this, to avoid increased assembly effort.
  • the snap ring shown in FIG. 5 has four legs and transitions in the form of a segment of a circle between them, which increase its rigidity.
  • FIG. 6 shows a 3-leg snap ring with transitions in the shape of a segment of a circle, the inside and outside diameters of which are dimensioned analogously to FIG. 3, but the large gap dimension b of which allows very simple assembly with high elasticity against expansion.
  • the circular-arc-shaped transitions between the individual legs enable a secure guidance of the locking rings 59 in the groove receiving them due to their larger contact surface on the outer diameter compared to edge transitions.
  • FIGS. 7 and 8 show further exemplary embodiments of the axial securing of the rocker arm pin 67 on the tappet pin 25, the securing ring 59 in FIG. 7 being guided directly in a groove 81 in the tappet pin 25.
  • the rocker pin 67 is axially secured via a shaped sheet metal part 81 designed as an annular sleeve, which is locked onto the tappet pin via locking elements (73) designed as spring tongues that engage in a groove 75 on the outer circumference of the head of the ball socket 63 is and of sen upper, protruding beyond the tappet pin 25 end piece 83 is angled so that it engages behind the ball head 65 of the rocker arm pin 67 and thus secures it against axial slipping out of the pan 63.
  • locking elements (73) designed as spring tongues that engage in a groove 75 on the outer circumference of the head of the ball socket 63 is and of sen upper, protruding beyond the tappet pin 25 end piece 83 is angled so that it engages behind the ball head 65 of the rocker arm pin 67 and thus secures it against axial slipping out of the pan 63.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP93116228A 1992-11-07 1993-10-07 Dispositif d'injection de combustible, in particulier pompe-injecteur pour moteurs à combustion interne Expired - Lifetime EP0597249B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4237682A DE4237682A1 (de) 1992-11-07 1992-11-07 Kraftstoffeinspritzeinrichtung, insbesondere Rumpedüse für Brennkraftmaschinen
DE4237682 1992-11-07

Publications (2)

Publication Number Publication Date
EP0597249A1 true EP0597249A1 (fr) 1994-05-18
EP0597249B1 EP0597249B1 (fr) 1996-05-22

Family

ID=6472372

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93116228A Expired - Lifetime EP0597249B1 (fr) 1992-11-07 1993-10-07 Dispositif d'injection de combustible, in particulier pompe-injecteur pour moteurs à combustion interne

Country Status (4)

Country Link
US (1) US5402764A (fr)
EP (1) EP0597249B1 (fr)
JP (1) JPH06200854A (fr)
DE (2) DE4237682A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0682178A3 (fr) * 1994-05-02 1996-03-06 Cummins Engine Co Inc Liaison par bille pour systèmes d'entraînement dans les moteurs de véhicules.
CN104612874A (zh) * 2014-12-10 2015-05-13 重庆福欧机械有限公司 一种喷油泵油量控制自动微调机构

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5682861A (en) * 1996-05-23 1997-11-04 Caterpillar Inc. Fluid seal for cyclic high pressures within a fuel injection
US6688536B2 (en) * 1997-10-22 2004-02-10 Caterpillar Inc Free floating plunger and fuel injector using same
GB2330626A (en) 1997-10-22 1999-04-28 Caterpillar Inc Tappet retention for a fuel injector
US5878710A (en) * 1998-07-20 1999-03-09 Caterpillar Inc. Fuel injection shutdown system
US6003790A (en) * 1998-10-14 1999-12-21 Ford Global Technologies, Inc. Pre-load mechanism having self-mounting coil spring
US6607149B2 (en) * 2001-12-28 2003-08-19 Robert Bosch Fuel Systems Corporation Follower assembly with retainer clip for unit injector
CN103670857A (zh) * 2012-09-25 2014-03-26 上海电装燃油喷射有限公司 燃油喷射泵中柱塞偶件o型圈的装配方法
AT515737B1 (de) * 2014-05-12 2018-06-15 Avl List Gmbh Nockenfolgeeinrichtung für eine brennkraftmaschine
CN105422346B (zh) * 2015-12-11 2018-03-13 中国北方发动机研究所(天津) 大流量、高转速转子式高压共轨变量泵用柱塞偶件

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191224127A (en) * 1912-10-22 1913-08-21 James Mckechnie Improvements in and relating to the Injection of Liquid Fuel in Internal Combustion Engines.
GB375151A (en) * 1930-10-08 1932-06-23 Bernhard Bischof Improvements in or relating to fuel injection pumps for internal combustion engines
GB2113775A (en) * 1982-01-15 1983-08-10 Bosch Gmbh Robert Fuel injection pump
DE3943419A1 (de) * 1989-12-30 1991-07-04 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen, insbesondere pumpeduese
WO1992010668A1 (fr) * 1990-12-11 1992-06-25 Lucas Industries Public Limited Company Pompe d'injection de carburant

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA547612A (fr) * 1957-10-15 Seifert Richard Systeme de commande d'injection de carburant pour moteurs a combustion interne
GB211377A (en) * 1923-04-25 1924-02-21 Philip Boyce Taneborne Improvements in washers for coach bolts
US2897805A (en) * 1957-11-08 1959-08-04 Bundy Tubing Co Tubular push rod and method of making same
US4206734A (en) * 1977-12-27 1980-06-10 Cummins Engine Company, Inc. Adjustable timing mechanism for fuel injection system
US4407241A (en) * 1980-12-31 1983-10-04 Cummins Engine Company, Inc. Expandable hydraulic tappet with a variable exit valve
US4531672A (en) * 1983-05-13 1985-07-30 Cummins Engine Company, Inc. Solenoid operated unit injector having distinct timing, metering and injection periods
US4794894A (en) * 1987-03-05 1989-01-03 Cummins Engine Company, Inc. Ceramic tipped pivot rod and method for its manufacture
DE3813320A1 (de) * 1988-04-08 1989-10-19 Voest Alpine Automotive Pumpenduese fuer dieselmotoren
US4864983A (en) * 1988-08-17 1989-09-12 Caterpillar Inc. Pushrod retainer
US4966108A (en) * 1989-04-28 1990-10-30 Cummins Engine Company, Inc. Sintered ceramic ball and socket joint assembly
US5320278A (en) * 1993-07-26 1994-06-14 Cummins Engine Company, Inc. High pressure fuel injector with fuel drainage valve

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191224127A (en) * 1912-10-22 1913-08-21 James Mckechnie Improvements in and relating to the Injection of Liquid Fuel in Internal Combustion Engines.
GB375151A (en) * 1930-10-08 1932-06-23 Bernhard Bischof Improvements in or relating to fuel injection pumps for internal combustion engines
GB2113775A (en) * 1982-01-15 1983-08-10 Bosch Gmbh Robert Fuel injection pump
DE3943419A1 (de) * 1989-12-30 1991-07-04 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen, insbesondere pumpeduese
WO1992010668A1 (fr) * 1990-12-11 1992-06-25 Lucas Industries Public Limited Company Pompe d'injection de carburant

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0682178A3 (fr) * 1994-05-02 1996-03-06 Cummins Engine Co Inc Liaison par bille pour systèmes d'entraînement dans les moteurs de véhicules.
CN104612874A (zh) * 2014-12-10 2015-05-13 重庆福欧机械有限公司 一种喷油泵油量控制自动微调机构
CN104612874B (zh) * 2014-12-10 2017-01-25 重庆福欧机械有限公司 一种喷油泵油量控制自动微调机构

Also Published As

Publication number Publication date
US5402764A (en) 1995-04-04
JPH06200854A (ja) 1994-07-19
EP0597249B1 (fr) 1996-05-22
DE4237682A1 (de) 1994-05-11
DE59302680D1 (de) 1996-06-27

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