EP0185914A2 - Pompe d'injection de carburant pour moteurs à combustion interne - Google Patents

Pompe d'injection de carburant pour moteurs à combustion interne Download PDF

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Publication number
EP0185914A2
EP0185914A2 EP85114587A EP85114587A EP0185914A2 EP 0185914 A2 EP0185914 A2 EP 0185914A2 EP 85114587 A EP85114587 A EP 85114587A EP 85114587 A EP85114587 A EP 85114587A EP 0185914 A2 EP0185914 A2 EP 0185914A2
Authority
EP
European Patent Office
Prior art keywords
pump
pump piston
delivery
fuel injection
piston
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
EP85114587A
Other languages
German (de)
English (en)
Other versions
EP0185914B1 (fr
EP0185914A3 (en
Inventor
Josef Güntert
Walter Häfele
Helmut Dr. Dipl.-Ing. Tschöke
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
Priority to AT85114587T priority Critical patent/ATE50320T1/de
Publication of EP0185914A2 publication Critical patent/EP0185914A2/fr
Publication of EP0185914A3 publication Critical patent/EP0185914A3/de
Application granted granted Critical
Publication of EP0185914B1 publication Critical patent/EP0185914B1/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
    • F02M59/20—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
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/361—Valves being actuated mechanically

Definitions

  • the invention relates to a fuel injection pump according to the preamble of the main claim.
  • Slider-controlled pumps are primarily used for large capacities at high pressures, i.e. for larger, less fast-running motors.
  • deviations from the target injection values not only have an effect on the engine running poorly, but can very easily lead to correspondingly costly engine damage.
  • the connecting channel is designed as a bore in the pump cylinder liner, opens into a suction chamber of the injection pump surrounding this cylinder liner and is blocked by the pump piston after a forward stroke has been completed, after which the fuel delivery to the engine can start.
  • the pump working space is filled with fuel through this hole, while the position of the hole determines the start of delivery during the pressure stroke of the pump.
  • the end of delivery and thus the delivery rate is determined by the respective position of the control spool.
  • the mouth of a volume control channel running in the pump piston emerges from the inner bore of the control slide for the delivery end.
  • the fuel injection pump according to the invention with the characteristic features of the main adapter has the advantage that the effective fuel delivery to the engine is terminated regardless of the fuel control performed by the control slide after a certain pump piston stroke. At the same time, this limits the maximum possible delivery volume of the injection pump, which in particular prevents the engine from running away. In addition, it can be achieved that the high-pressure delivery is ended by timely opening of the relief channel before the roller of the roller tappet moves from the straight (tangential) to the curved section of the drive cam of the injection pump. A dangerous shifting of the end of delivery towards "late” with the consequence of the disadvantages described above is prevented by the invention, without there being disadvantages for quantity control or engine operation.
  • control slide quantity control By appropriately assigning the control slide quantity control, it can advantageously be achieved that the fuel delivery is reduced to zero when an undesired extreme position of the control slide is assumed. This is achieved if the connecting channel arranged in the pump cylinder is opened by the relief channel before the mouth of the quantity control channel dips into the control slide for the start of delivery.
  • the position of the inlet of the connecting channel in the pump cylinder can be arranged differently with respect to the position of the pump piston controlling it.
  • the earliest start of delivery is also controlled by the connecting channel, in that the input of the connecting channel is only blocked after a forward stroke of the pump piston has been completed, so that a pressure can only be built up in the pump work space after this at the earliest.
  • the connection channel serves. thereby additionally as a possibility of filling up the pump work space, namely as long as the pump piston is close to its bottom dead center position.
  • the mouth of the relief channel can either always remain within the bore of the pump cylinder that receives the pump piston, or it can also emerge from the pump cylinder with the advantage of additional filling of the pump working space in the bottom dead center position. In this case, however, after the maximum working stroke of the pump piston has been covered, the mouth of the relief channel opens the input of the connecting channel in order to interrupt the fuel delivery to the engine. In this way, the maximum delivery stroke and thus the maximum delivery volume is limited by the relief channel and the connecting channel, and it is also prevented that the start of delivery begins too early, it being known that an early start of delivery is usually more damaging to the motor than a late start of delivery.
  • the entrance of the connecting channel is covered by the outer surface of the pump piston and is opened by the mouth of the relief channel after the pump piston has covered the defined stroke.
  • the connecting channel does not lead to the suction space, but only to a drain collecting space.
  • the opening of the relief channel arranged on the pump piston can either only dip into the bore of the pump cylinder after a certain forward stroke or can always remain within the bore of the pump cylinder receiving the pump piston, i.e. do not even emerge from the pump cylinder in the stroke area around bottom dead center .
  • the start of production can be determined by immersing the mouth into this bore, in the second case, this start of production must be achieved by other means, for example the volume control slide.
  • the mouth of the relief channel can be designed appropriately and thus in different ways.
  • An annular groove or a transverse groove can serve as the opening, which are then connected to the pump work space via a transverse bore and a longitudinal bore that run in the pump piston. If the pump piston can be rotated to change the quantity, the upper boundary edge of the control groove can be stepped and / or run obliquely to the pump piston axis, so that turning the pump piston causes a change in the opening stroke between the discharge channel mouth and the connecting channel inlet. In this way, the latest end of delivery in connection with the change in the delivery rate can also be changed.
  • FIG. 1 shows a longitudinal section through a fuel injection pump
  • FIGS. 2 to 5 show different assignments of the connecting duct and relief duct as a detail and on an enlarged scale from FIG. 1
  • FIGS. 6 to 9 show three variants of the discharge duct mouth on a piston section, and lo a functional diagram.
  • a plurality of cylinder liners 2 - only one of which is shown - are embedded in series in a housing 1, in which pump pistons 3, with the interposition of a roller tappet 4 with roller 5, by a camshaft 6 against the force of a spring 7 are driven for their axial movement forming the working stroke.
  • the cylinder liner 2 there is a recess 8 which receives a control slide 9 which is axially displaceable on the pump piston 3.
  • the individual control slides 9, which are displaceably arranged on the respective pump pistons, of which only one is also shown, are axially displaced together by a control rod 10.
  • the control rod 10 is rotatably mounted for this purpose in the housing 1 and has a driving link for each control slide 9 in the form of a clamping ring 12 provided with a head 11, which is clamped to the control rod 10 by a clamping screw 13, the head 11 being in an annular groove 14 of the control slide 9 engages.
  • the pump piston 3 and the cylinder liner 2 delimit a pump work chamber 16, from which a pressure channel 17, in which a compensating valve 18 is arranged, leads to a pressure line, not shown, which ends at an injection nozzle of the internal combustion engine.
  • transverse bore 21 opening into the pump working space 16 and two transverse bores 21 and 22, of which the transverse bore 21 is only shown in plan view in FIG.
  • the transverse bore 21 opens into a transverse groove 23 provided in the lateral surface of the pump piston 3, which in this variant shown in FIG. 1 is formed by grinding the piston lateral surface and is ge together with the transverse groove 21 and the section of the blind bore 19 leading to the pump working space 16 forms a relief channel.
  • the second transverse bore 22 opens into two inclined grooves 24, which are also arranged on the lateral surface of the pump piston 3, and longitudinal grooves 25, which, in conjunction with the control slide 9 and its inner bore 26 and a relief bore 27 arranged in the control slide 9, serve to control the delivery rate.
  • the pump piston 3 has at its lower end a flattened area 28 on which a driving member 31 which can be rotated in a known manner by a control rod 29 acts, so that an axial displacement of the control rod 29 causes the pump piston 3 to rotate.
  • the cylinder liner 2 In its central section, which also has the cutout 8, the cylinder liner 2 is surrounded by a suction space 32 provided in the housing 1, which is filled with fuel under low pressure. This suction chamber 32 is thus also connected to the grooves 23, 24 and 25, as long as these are not covered by the control slide 9 or the pump cylinder 33 of the cylinder liner 2.
  • the cylinder liner 2 In the cylinder liner 2 there is a radial bore 35 serving as a connecting channel, which connects the pump working chamber 16 to the suction chamber 32 as long as it is not blocked by the pump piston 3.
  • the pressure required for the injection only builds up in the pump working space 16 when the inflow channels between the suction space 32 and the pump working space 16 are blocked. As long as the fuel is pumped back to the pump suction chamber 32 from the pump work chamber 16 via these channels.
  • the closing of the quantity control channels during the pressure stroke depends on the axial position of the control slide 9 and the rotational position of the pump piston 3.
  • the blocking of the relief channel 19, 21, 23 or the connecting channel 35 depends solely on the stroke position of the pump piston 3, so that this control is to be considered independently of that by the control slide 9.
  • the control valve 9 controls the amount of fuel delivered to the engine in the usual way, depending on the rotational position of the pump piston 3 and thus depending on the distance between the upper control edge of the oblique grooves 24 and the relief bore 27, a differently long stroke of the pump piston 3 must be covered before by Open this volume control channel formed by blind bore 19, transverse bore 22 and grooves 24, 25, the high-pressure delivery and thus the injection is ended.
  • One for injection Sufficient pressure can only build up in the pump working space 16 when the longitudinal grooves 25 are immersed in the bore 26 of the control slide 9.
  • the control rod 29 is axially displaced by a speed controller, not shown, which can work with mechanical or electrical means, which results in a rotation of the driving element 31 and the pump piston 3.
  • This effective delivery stroke serving for injection can be shifted in time by axially displacing the control slide 9.
  • This described temporal shift of the effective delivery stroke by moving the control slide 9 is carried out in normal engine operation and only works properly if the control slide 9 is not moved to its extreme positions up or down within the recess 8, which is due, for example, to its own weight if the Drive of the control rod 12 controlling the start of injection can take place or if, for example when using an electrical control device, the control slide 9 is pushed upward beyond the normal working range due to errors thereof. Moving the control slide 9 into the lower extreme position leads to an early start of delivery, which can lead to their destruction in the engines usually supplied by such injection pumps if not counteracting safety measures be hit.
  • this risk is avoided by using the connecting channel 35 in cooperation with the relief channel 19, 21, 23.
  • the earliest start of delivery and the latest end of delivery and thus at the same time the maximum possible effective delivery stroke of the pump piston 3 is determined by the position of the inlet 36 of the connecting channel 35 in the pump cylinder 33 and the position of the mouth 23 (transverse groove) of the relief channel 19, 21 in the lateral surface of the pump piston 3 certainly. 2 to 5 show four different variants of this possible assignment of inlet 36 and mouth 23 on an enlarged scale.
  • control slide 9 were to occupy one of the extreme positions, it would not be possible to start spraying early because the earliest spray start (effective start of delivery) is determined by blocking the connecting channel 35 and this earliest possible start of spraying is selected such that damage to the motor cannot occur.
  • the effective delivery stroke of the pump piston 3 can at most be long enough until the mouth 23 of the relief channel 19, 21, 23 comes into overlap with the input 36 of the connecting channel 35. This limits the maximum possible delivery rate per injection stroke and also the latest possible end of delivery. On the one hand, this avoids that an inadmissibly large amount of fuel is injected even in the extreme positions of the control slide 9 and, on the other hand, this means that the delivery rate is reduced by the end of delivery independent of the position of the control slide 9 if the start of the delivery is determined too late by the control slide 9.
  • control slide 9 assumes its upper extreme position, for which it causes a late start of delivery, the entrance 36 to the connecting channel 35 is already blocked at this start of delivery, with the consequence of the early control by the relief channel 19, 21, 23, which accordingly reduces the injection quantity
  • the assignment of these controls can be selected so that at least in one extreme position of the control slide 9, no more fuel is injected by the pump.
  • the pump piston shown in FIGS. 3 to 5 is shown in its bottom dead center position UT in accordance with FIG.
  • the mouth 123 of the transverse bore 121 of the relief duct 19, 121, 123 also does not emerge from the cylinder bore 33 in UT, so that this relief duct cannot assume any filling function of the pump work space 16.
  • the function remains the same as described above, since the start of funding only when the input 36 of the connection is covered channel 35 is determined by the pump piston and the latest delivery end by opening this channel through the opening 123 of the transverse bore 121.
  • this variant compared to the embodiment described in FIGS.
  • either the effective delivery stroke can be shortened or the pump cylinder, for example, to achieve a longer overlap to the pump piston 3 can be extended.
  • the input 136 of the connecting channel 135 remains blocked by the pump piston 3 even in sub-station, so that the start of delivery is determined by the relief channel 19, 21, 23 and the end of delivery by covering the mouth 23 with the entrance 136 of the channels .
  • the maximum possible effective delivery stroke is determined by the input 136 of the connecting channel 135 and the mouth 23 of the relief channel 19, 21.
  • the mouth 123 of the relief duct 19, 121 and the inlet 136 of the connecting duct 135 remain blocked in UT by the cylinder liner 33 and the pump piston 3.
  • the earliest start of funding must therefore be controlled by other means.
  • the end of delivery and thus the maximum possible delivery rate is determined by the position of mouth 123 and entrance 136.
  • the channels 19, 121 and 135 cannot be used to fill up the pump work space 16 during the suction stroke or in the bottom of the pump piston 3.
  • the mouth is again formed as a flat 223 shown in plan view, into which the transverse bore 21 opens and whose upper and lower boundary edges 137 and 138 do not run parallel to one another, in contrast to the exemplary embodiment shown in FIG. 6, but instead enclose a certain angle.
  • the mouth of the transverse bore 21 is designed as an annular groove machined into the outer surface of the pump piston 3 with parallel boundary edges.
  • the upper boundary edge 237 of this annular groove 423 is designed in a stepped manner, so that the delivery end can also be changed depending on the load depending on the rotational position of the pump piston 3.
  • a corresponding oblique control edge can also be provided.
  • the load capacity of cam drives is determined by the maximum permissible Hertzian pressures occurring there between the drive part (cam) and output part (roller).
  • the roller 5 of the roller tappet 4 on a curved path of the cam 39 (FIG. 1) of the camshaft the maximum transferable forces are lower than when the roller 5 runs on the straight section 41 of the cam 39, the so-called tangent area.
  • the roller 5 of the roller tappet 4 only runs on the tangent region 41 of the cam 39 for the effective useful stroke.
  • the cam 39 points straight down (UT of the pump piston 3), so that the roller 5 of the roller tappet 4 rests on the base circle 42. If the camshaft 6 rotates in the direction of the arrow, the pump piston remains in the illustrated UT position for this twist angle ⁇ up to approximately 115 ° NW. During this time, the pump work space 16 is filled with fuel. For the subsequent angle of rotation, here up to approximately 160 ° NW, the roller 5 rolls on the straight section 41 of the cam 39. Then a curved section 43 of the cam 39 follows again, shortly before the pump piston then assumes its top dead center OT after 180 ° NW. Then the suction stroke of the pump piston follows, also at 180 ° NW.
  • the stroke h of the pump piston 3 (ordinate) is plotted against the degree of rotation ⁇ in 0 NW (abscissa).
  • Q is the delivery curve of the pump, which can be seen that the fuel displacement through the pump piston 3 begins at ⁇ ⁇ 115 ° NW and only gradually increases, so that a uniform delivery per angle of rotation is only achieved at ⁇ ⁇ 145 ° NW.
  • the uniformly high pressure required for injection can therefore only be achieved in the rotation angle section between ⁇ ⁇ 145 ° and 160 ° NW.
  • the control slide 9 can thus determine the start of delivery and / or the end of delivery only as long and within this range between points a and b, as long as the earliest start of delivery or the latest end of delivery is not already carried out by the control between relief channel 19, 21 and / or connecting channel 36 . respectively. That is to say transferred to FIG. 10 that the start and end of the delivery cannot be influenced by the control slide 9 in the piston stroke sections a a and b b.
  • the start of delivery even if the longitudinal groove 25 is already blocked, can only begin when the stroke a has been covered by the pump piston.
  • the rotational position of the piston that is, depending on the set maximum delivery rate, it is only possible to inject from this stroke a until, after the stroke c has been covered, for example, the relief bore 27 in the control slide 9 is opened by the oblique groove 24, which leads to a corresponding pressure reduction in the pump working space 16 leads.
  • the tangent area of the curve Q used between points A and C.
  • the longitudinal groove 25 of the quantity control channel also dips into the control slide 9 relatively late, for example after the stroke d has been covered, after which the high pressure can build up only in the pump work chamber 16.
  • the effective delivery stroke is thus limited to the stroke section between d and b, since the pressure in the pump working chamber 16 is already reduced at b via the relief duct 19, 21 and the connecting duct 35 and the injection is thus interrupted.
  • the tangent area of curve Q between points D and B is thus used for the effective delivery stroke.
  • the maximum delivery volume set by the rotational position is reduced by opening the pump work chamber 16 at point B, which in extreme cases can lead to zero delivery , for example, when the start of delivery D coincides with the end of delivery B, namely when the connecting channel 35 opens the relief channel 19, 21 before the longitudinal groove 25 of the volume control channel dips into the control slide 9.

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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)
EP85114587A 1984-12-24 1985-11-16 Pompe d'injection de carburant pour moteurs à combustion interne Expired - Lifetime EP0185914B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85114587T ATE50320T1 (de) 1984-12-24 1985-11-16 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3447374 1984-12-24
DE19843447374 DE3447374A1 (de) 1984-12-24 1984-12-24 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Publications (3)

Publication Number Publication Date
EP0185914A2 true EP0185914A2 (fr) 1986-07-02
EP0185914A3 EP0185914A3 (en) 1988-01-07
EP0185914B1 EP0185914B1 (fr) 1990-02-07

Family

ID=6253878

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85114587A Expired - Lifetime EP0185914B1 (fr) 1984-12-24 1985-11-16 Pompe d'injection de carburant pour moteurs à combustion interne

Country Status (5)

Country Link
US (1) US4708114A (fr)
EP (1) EP0185914B1 (fr)
JP (1) JPS61157753A (fr)
AT (1) ATE50320T1 (fr)
DE (2) DE3447374A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0185915A3 (fr) * 1984-12-24 1988-01-07 Robert Bosch Gmbh Pompe d'injection de carburant pour moteurs à combustion interne

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0301222B1 (fr) * 1987-07-25 1992-05-06 Robert Bosch Gmbh Pompe d'injection de combustible pour moteurs à combustion interne
DE3811845A1 (de) * 1988-04-08 1989-10-19 Voest Alpine Automotive Pumpeduese fuer dieselmotoren
DE3813320A1 (de) * 1988-04-08 1989-10-19 Voest Alpine Automotive Pumpenduese fuer dieselmotoren
US5080564A (en) * 1989-02-08 1992-01-14 Diesel Kiki Co., Ltd. Prestroke control device for fuel injection pumps
JP2543729Y2 (ja) * 1990-09-13 1997-08-13 三菱自動車工業株式会社 ディーゼル機関の燃料噴射装置
DE4100093A1 (de) * 1991-01-04 1992-07-09 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen mit last- und/oder drehzahlabhaengigem einspritzverlauf
JPH05272429A (ja) * 1992-03-25 1993-10-19 Mitsubishi Motors Corp 燃料噴射装置
JPH10281033A (ja) * 1997-04-03 1998-10-20 Zexel Corp 燃料噴射ポンプのスピル制御装置
DE102007034036A1 (de) * 2007-07-20 2009-01-22 Robert Bosch Gmbh Kraftstoffhochdruckpumpe mit Rollenstößel

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2147390A (en) * 1934-04-17 1939-02-14 Provencale De Const Aeronautiq Fuel feed pump
US2746443A (en) * 1953-02-20 1956-05-22 Texas Co Fuel injection pump
FR91309E (fr) * 1965-11-09 1968-05-24 Inst Francais Du Petrole Dispositif de double injection
US3312209A (en) * 1964-11-12 1967-04-04 Bosch Arma Corp Fuel delivery system
FR1521391A (fr) * 1967-01-16 1968-04-19 Mikuni Kogyo Company Ltd Pompe à injection ou analogue
US3712763A (en) * 1970-09-18 1973-01-23 Caterpillar Tractor Co Sleeve metering collar adjusting lever
DE3017730A1 (de) * 1980-05-09 1981-11-12 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3018791A1 (de) * 1980-05-16 1981-11-26 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3447375A1 (de) * 1984-12-24 1986-07-03 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0185915A3 (fr) * 1984-12-24 1988-01-07 Robert Bosch Gmbh Pompe d'injection de carburant pour moteurs à combustion interne

Also Published As

Publication number Publication date
EP0185914B1 (fr) 1990-02-07
EP0185914A3 (en) 1988-01-07
ATE50320T1 (de) 1990-02-15
JPH0561465B2 (fr) 1993-09-06
US4708114A (en) 1987-11-24
DE3575979D1 (de) 1990-03-15
DE3447374A1 (de) 1986-07-10
JPS61157753A (ja) 1986-07-17

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