EP0336925B1 - Pumpedüse für Dieselmotoren mit Steuerhülse - Google Patents

Pumpedüse für Dieselmotoren mit Steuerhülse Download PDF

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Publication number
EP0336925B1
EP0336925B1 EP89890092A EP89890092A EP0336925B1 EP 0336925 B1 EP0336925 B1 EP 0336925B1 EP 89890092 A EP89890092 A EP 89890092A EP 89890092 A EP89890092 A EP 89890092A EP 0336925 B1 EP0336925 B1 EP 0336925B1
Authority
EP
European Patent Office
Prior art keywords
pump
piston
control sleeve
element body
track
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
EP89890092A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0336925A1 (de
Inventor
Maximilian Dipl.-Ing. Kronberger
Eugen Drummer
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.)
Automotive Diesel GmbH
Original Assignee
Automotive Diesel 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 Automotive Diesel GmbH filed Critical Automotive Diesel GmbH
Priority to AT89890092T priority Critical patent/ATE70596T1/de
Publication of EP0336925A1 publication Critical patent/EP0336925A1/de
Application granted granted Critical
Publication of EP0336925B1 publication Critical patent/EP0336925B1/de
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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/243—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movement of cylinders relative to their pistons
    • F02M59/246—Mechanisms therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention relates to a pump nozzle for diesel engines, having an injection pump element which has a fixed pump element body and a pump piston arranged therein and driven by a camshaft and which is combined with an injection nozzle to form a unit to be assigned to a respective motor cylinder, the pump piston being provided by a control sleeve is enclosed, which is adjustable to change the start of injection depending on the operating parameters of the engine in the direction of the axis of the pump piston by means of an adjusting force, the pump piston being rotatable relative to the control sleeve for adjusting the delivery rate and the control sleeve being secured against rotation relative to the pump element body.
  • Such a control sleeve usually has a control edge lying in a normal plane to the pump piston axis, which controls the start of injection.
  • a sloping control edge of the control sleeve or of the pump piston determines the end of injection and thus the injection quantity as a function of the rotational position of the pump piston relative to the control sleeve.
  • Such a pump nozzle has become known from DE-OS 3143073, in which the control sleeve is axially adjustable for the purpose of changing the start of injection.
  • the control sleeve is adjusted directly by means of a hydraulic piston. Since the control sleeve is adjusted directly by the hydraulic piston, the adjustment travel of the control sleeve is equal to the adjustment travel of the hydraulic piston. Because the adjustment path of the control sleeve is small, only small adjustment paths of the hydraulic piston are available for the adjustment of the control sleeve, and such a regulation is therefore not sensitive and precise.
  • the hydraulic piston is connected to the control sleeve via a linkage.
  • the play in the linkage also makes the adjustment of the control sleeve imprecise.
  • the control sleeve is guided directly on the pump piston, so that wear between the control sleeve and the pump piston is promoted.
  • the control sleeve is guided on the pump piston over a relatively small guide length and there is therefore a risk of the control sleeve being covered on the pump piston, which increases the wear on the pump piston and control sleeve and also reduces the precision of the control.
  • the axially adjustable hydraulic piston surrounds the pump piston and is itself designed as a control sleeve. It is therefore also in this embodiment, the adjustment of the hydraulic piston equal to the adjustment of the control sleeve and also seals are required, which also affect the precision and sensitivity of the control due to the friction.
  • the object of the invention is to provide a pump nozzle in which the start of delivery can be adjusted individually and independently of the other pump nozzles precisely, sensitively and reproducibly and can be adapted to different operating parameters of the engine, the setting device also being suitable for electronic control.
  • the invention consists essentially in that on the pump element body a rotatable about the axis of the pump piston regulating member is axially immovable and rotatable relative to the control sleeve or to the part connected to it, on which the adjusting force acts, and that of the parts rotatable relative to one another - namely control sleeve or with this connected part and regulating member - one part is equipped with at least one path which, in axial projection, surrounds the axis of the pump piston and is essentially circular, which, at least over part of its length, includes a pitch angle with a normal plane to the axis of the pump piston, and the other part has interacting guide element with this track.
  • the track can be arranged on the control sleeve or on a part connected to it, the regulating member carrying the guide element which cooperates with the track.
  • the control sleeve or the part connected to it can also carry the guide element and the regulating member can have the track. Since the control sleeve or the part connected to it is axially displaceable and secured against rotation on the pump element body and the regulating member is rotatably and axially immovably mounted on the pump element body, a relative rotation of the two parts in both cases results in a lifting or lowering of the control sleeve and thus an adjustment of the Start of injection. Since this path is essentially circular in axial projection, the guide element remains in contact with the path at all relative rotational positions.
  • the interaction of the guide element with the web results in a translation between the twisting movement of the regulating member and the lifting movement of the control sleeve.
  • the size of this ratio depends on the size of the pitch angle, which the path includes with a normal plane to the axis.
  • This translation can increase the precision and sensitivity of the adjustment of the start of funding.
  • the path can, for example, enclose an incline angle of 0 ° to 80 ° with a plane perpendicular to the axis of the pump piston.
  • the path can, for example, be a helical surface running along a helical line.
  • the gear ratio remains throughout
  • the range of rotation of the control element is the same and the stroke of the control sleeve is proportional to the angle of rotation of the control element.
  • the web can also have sections arranged one behind the other with differently sized and / or differently directed gradients, the gradient angle being able to be zero at certain points on the web. In this case it is possible to adapt the start of funding to a wide variety of conditions.
  • one part can have a groove delimited by two parallel tracks, the guide element being hook-shaped and engaging with the hook part in a form-fitting manner in the groove.
  • One part can also have a web delimited by two parallel tracks, the guide element being designed as a claw that engages around the web in a form-fitting manner.
  • the control sleeve can also be loaded by a force acting in the axial direction, in particular a spring, which holds the web in contact with the guide element. In this case, a game in the transmission is switched off by the resilient system.
  • Such a path can be formed, for example, on the lower edge of the control sleeve, this path being scanned by a correspondingly shaped guide element of the regulating member.
  • the control sleeve can be prevented from rotating relative to the fixed pump element body by a simple sliding guide, for example by a rod connected to the pump element body.
  • the anti-rotation lock of the control sleeve can also be formed by a ball guide, the balls of which are arranged between axially parallel surfaces of the control sleeve and the pump element body.
  • the regulating member which can be rotated about the axis of the pump piston can be formed, for example, by the rotor of an electrical actuator or can be connected to it. According to a preferred embodiment of the invention, however, the regulating member is one or the like in an outer sleeve.
  • tightly sealed annular groove of the pump element body tightly guided ring segment-shaped control piston is formed, which can be acted upon by a hydraulic medium against a restoring force, in particular a spring force.
  • the annular groove for forming a working space for the control piston in the form of a ring segment can be sealed at one point by a part of the pump element body or by a part connected to it.
  • a spring space can be provided in the groove on the side of the part closing the groove opposite the working space in the groove for a return pressure spring which is supported against this part and against the ring segment-shaped control piston.
  • the return spring can also be a torsion spring supported against the pump element body and against the ring segment-shaped control piston.
  • the torsion spring is expedient against an adjusting disk or the like which is rotatably connected to the pump element body and can be locked in its rotational position. Adjustment element supported.
  • a pin can be connected, which can be used in several mutually offset bores of the pump element body, which is easier Way allows the adjustment of the spring tension when installing the pump.
  • the arrangement can be made according to an advantageous embodiment of the invention so that the ring-shaped control piston is acted upon by fuel from a pressure-controlled space in which the pressure is dependent on the operating parameters of the engine, for example by a controlled by electronics Valve, in particular a switching valve, is regulated.
  • the fuel can be supplied to the pressure-controlled space by a separate pump or, if necessary, also from the intake space or the control space of the pump nozzle.
  • the injection pump element therefore expediently has an intake space and a control space, the control space being separated from the intake space and connected to a return line via bores.
  • FIG. 1 and 2 show an embodiment of the pump nozzle, wherein FIG. 1 shows an axial section along line II of FIG. 2 and FIG. 2 shows a cross section along line II-II of FIG. 1.
  • Fig. 3 shows a cross section in the same way as Fig. 2 through a modified embodiment. 4 and 5 show a detail, FIG. 4 a partial section corresponding to FIG. 5 and FIG. 5 a view in the direction of arrow V of FIG. 4.
  • Fig. 6 shows in partial section corresponding to FIG. 1, a modified design.
  • Fig. 7 shows on a larger scale a modified design in section along line II-II of Fig. 1.
  • Fig. 8 and 9 show two variants in partial sections through the axis of the pump nozzle.
  • FIGS. 10 and 11 show a schematic representation of a modified embodiment of the anti-rotation lock of the control sleeve, FIG. 11 showing a cross section along line XI-XI of FIG. 10 and FIG. 10 a view in the direction of arrow X of FIG. 11.
  • FIGS. 12 and 13 show a modified embodiment in the form of a cutout in the area of the control sleeve, FIG. 13 showing a view in the direction of arrow XIII of FIG. 12.
  • FIGS. 14 and 15 show another modified embodiment in the form of a cutout in the area of the control sleeve, FIG. 15 showing a view in the direction of arrow XV of FIG. 14.
  • 16 and 17 show another modified embodiment, wherein FIG. 16 shows a partial axial section through the pump nozzle and FIG. 17 shows a view in the direction of arrow XVII of FIG. 16.
  • Fig. 18 shows a diagram for the regulation of the pressure of the hydraulic medium to act on the ring segment piston.
  • 1 represents the pump piston, which is driven by a camshaft, not shown, via a rocker arm and a tappet 2.
  • the return spring 3 of the pump piston acts on the pump piston 1 via a spring plate 4 and is guided in a guide bush 5.
  • 6 is the high pressure chamber of the pump and 7 is the injection nozzle. 8 is the suction hole. 9 is a crank arm for the rotation of the piston. 10 is the pump element body.
  • control sleeve 11 is the control sleeve, which surrounds the pump piston 1 and has the control openings or control edges.
  • the piston 1 has an axial bore 12, from which a radial bore 13 extends. If the control edge 14 of the control sleeve 11 closes the radial bore 13, the production begins. As soon as the oblique edge, not shown, of the control sleeve 11 releases the transverse bore 13 of the piston 1, the delivery stroke is ended and the fuel is discharged from the high-pressure chamber 6.
  • the regulating member 15 is a regulating member which is rotatably guided in a groove 16 of the pump element body 10 about the axis of the pump piston 1 and which is designed as a piston 15 in the form of a ring segment.
  • the annular groove 16 is closed off by an outer sleeve 17 which tightly surrounds the annular groove 16 of the pump element body 10 and forms a working space 18 which is delimited by an end face 19 of the ring segment-shaped piston 15 and by a part 20 rigidly connected to the pump element body 10.
  • This working chamber 18 is supplied via a bore 21 in the part 20 hydraulic pressure medium under a controllable pressure, so that the annular segment-shaped piston 15 can be rotated in the annular groove 16 of the pump element body 10 under the pressure of the hydraulic medium.
  • torsion spring 22 is a torque-transmitting spring or torsion spring which acts on the piston 15 and is supported against the pump element body 10.
  • the hydraulic medium in the working space 18 acts against the bias of the torsion spring 22 and this torsion spring 22 therefore represents a return spring for the piston 15 in the form of a ring segment.
  • the hook of this guide element 23 engages in an annular groove 24 on the circumference of the control sleeve 11, which is delimited by parallel tracks 25, which tracks are formed by helical helical surfaces in the embodiment of the drawing.
  • the control sleeve 11 is in turn secured against rotation by a guide pin 26 engaging in it, which is rigidly connected to the pump element body 10, and by the rotation of the ring
  • the control sleeve 23 raises and lowers the segment-shaped piston 15 via the guide element 23, with the result that the start of injection is changed as a function of the hydraulic pressure made effective in the working space 18.
  • the outer sleeve 17 is rigidly connected to the pump element body 10.
  • 27 is a shim against which the torsion spring 22 is supported.
  • the pump element body 10 has bores (not shown) which are arranged at a distance from one another along a circular arc and into which a pin 28 connected to the adjusting disk 27 is optionally inserted.
  • 29 is a screw ring which can be screwed into the outer sleeve 17 and which holds the adjusting disk 27.
  • 30 is a free space in the annular groove 16, which enables the rotation of the ring segment-shaped piston 15.
  • 31 is a slotted sealing ring inserted between the base of the annular groove 16 and the ring segment-shaped piston 15.
  • the embodiment according to FIG. 3 differs from the embodiment according to FIG. 2 in that the part 32 closing the annular groove with the pump element body 10 consists of one piece, while according to FIG. 2 the part 20 is a separate part rigidly connected to the pump element body 10 Is part.
  • FIG. 4 and 5 show on a larger scale the detail of the piston 15 in the form of a ring segment with the guide element 23 and the lower part of the control sleeve 11.
  • the guide element 23 has a hook 33 which engages in the groove 24 delimited by the tracks 25.
  • Fig. 5 it is shown that the helix, according to which the groove 24 runs, can also be designed to be kinked, which may appear expedient for certain control problems.
  • FIG. 6 shows an embodiment in which, instead of the groove 24 on the control sleeve 11, a helical web 34 is provided, which is delimited by the tracks 25.
  • the guide element 23 is formed with two claws 35 and 36 which grip around the web 34.
  • the embodiment according to FIG. 7 differs from the embodiment according to FIG. 2 in that a curved helical compression spring 37 is inserted into the space 30 instead of the torsion spring 22.
  • the helical compression spring 37 is supported against the part 20 rigidly connected to the pump element body 10 and acts on the end face 38 of the control piston 15 in the form of a ring segment counter to the hydraulic pressure in the working chamber 18 acting on the piston face 19.
  • the maximum position and the minimum position of the piston are 19b and 38a 15 indicated. At the lowest pressure in the working space 18, the end face 38 reaches the position 38a and at the highest pressure in the working space 18 the piston face 19 reaches the position 19b.
  • FIG. 8 shows the sealing ring 31 between the base of the ring groove 16 and the ring segment-shaped piston 15 in an arrangement in which the ring groove 16 has back turns 39. It is essential here that the sealing ring 31 has sharp edges 40 and 41. These sharp edges keep leakage within tolerable limits.
  • Fig. 9 shows an embodiment in which the annular groove 16 has no rear turns 39. At the back, the sealing ring 31 'bevels 42, while the sharp edge 40 is maintained.
  • this sealing ring 31 or 31 ' made of metal, for example also made of steel. Only the sharp edges 40 and 41 are essential.
  • control sleeve 11 is guided by balls 43, which run in grooves 43 'of the control sleeve 11, on axially parallel surfaces 44 of the pump element body 10. 45 is the control room.
  • This ball guide makes the axial displacement of the control sleeve 11 easier, which makes the control more sensitive.
  • the guide element 49 is hook-shaped and interacts with a track 50 which is formed on the control sleeve 11.
  • the control sleeve 11 is pressed upwards by compression springs 51, so that the web 50 is held non-positively in contact with the guide element 49.
  • the web 50 is here again in sections 50a arranged one behind the other and 50b subdivided with slopes of different sizes and directions.
  • FIG. 16 and 17 show an exemplary embodiment in which, in contrast to FIG. 1, the path 52, which is essentially circular in axial projection, is arranged on the regulating member formed by the piston 15 and the guide element 53 is arranged on the control sleeve 11.
  • the guide element 53 consists of a nose which interacts with the track 52.
  • the control sleeve 11 is pressed downward by compression springs 54, which are supported against the pump element body 10, and the guide element or the nose 53 is held in contact with the track 52.
  • FIG. 18 shows a diagram for the regulation of the pressure of the hydraulic medium which is supplied to the working space 18 of the piston 15 in the form of a ring segment.
  • the fuel is conveyed via a line 57 into a space 58 by a pump 56 supplied with fuel via a line 55.
  • This space 58 is connected via a switching valve 60 controlled by an electronic regulator 59 to a return line 61, which leads into the fuel tank 62.
  • This electronically controlled valve regulates the pressure in chamber 58 in accordance with the operating parameters of the engine. From this pressure-controlled space 58, the pressure-controlled fuel reaches the working space 18 of the piston 15 in the form of a ring segment via a line 63.

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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)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
EP89890092A 1988-04-08 1989-04-05 Pumpedüse für Dieselmotoren mit Steuerhülse Expired - Lifetime EP0336925B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89890092T ATE70596T1 (de) 1988-04-08 1989-04-05 Pumpeduese fuer dieselmotoren mit steuerhuelse.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3811846A DE3811846A1 (de) 1988-04-08 1988-04-08 Pumpeduese fuer dieselmotoren mit steuerhuelse
DE3811846 1988-04-08

Publications (2)

Publication Number Publication Date
EP0336925A1 EP0336925A1 (de) 1989-10-11
EP0336925B1 true EP0336925B1 (de) 1991-12-18

Family

ID=6351642

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89890092A Expired - Lifetime EP0336925B1 (de) 1988-04-08 1989-04-05 Pumpedüse für Dieselmotoren mit Steuerhülse

Country Status (5)

Country Link
US (1) US4960241A (enrdf_load_stackoverflow)
EP (1) EP0336925B1 (enrdf_load_stackoverflow)
JP (1) JPH01301954A (enrdf_load_stackoverflow)
AT (1) ATE70596T1 (enrdf_load_stackoverflow)
DE (2) DE3811846A1 (enrdf_load_stackoverflow)

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2118578A (en) * 1934-08-16 1938-05-24 Automotive Prod Co Ltd Fuel injection pump
US2740667A (en) * 1952-04-04 1956-04-03 Gen Motors Corp Compression operated fuel injector pump
US3999529A (en) * 1975-05-19 1976-12-28 Stanadyne, Inc. Multiple plunger fuel injection pump
US4108130A (en) * 1977-05-18 1978-08-22 Caterpillar Tractor Co. Fuel injection pump
DE3143073A1 (de) * 1981-10-30 1983-05-11 Robert Bosch Gmbh, 7000 Stuttgart Einspritzpumpe mit einstellbarem spritzzeitpunkt
AT380312B (de) * 1982-07-14 1986-05-12 Steyr Daimler Puch Ag Kraftstoff-einspritzaggregat fuer zylinder eines dieselmotors
DE3428174A1 (de) * 1984-07-31 1986-02-13 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Also Published As

Publication number Publication date
DE3811846C2 (enrdf_load_stackoverflow) 1991-06-06
ATE70596T1 (de) 1992-01-15
US4960241A (en) 1990-10-02
EP0336925A1 (de) 1989-10-11
DE3811846A1 (de) 1989-10-19
JPH01301954A (ja) 1989-12-06
DE58900575D1 (de) 1992-01-30

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