EP0262167A1 - Pompe d'injection de carburant pour moteurs a combustion interne. - Google Patents
Pompe d'injection de carburant pour moteurs a combustion interne.Info
- Publication number
- EP0262167A1 EP0262167A1 EP87901394A EP87901394A EP0262167A1 EP 0262167 A1 EP0262167 A1 EP 0262167A1 EP 87901394 A EP87901394 A EP 87901394A EP 87901394 A EP87901394 A EP 87901394A EP 0262167 A1 EP0262167 A1 EP 0262167A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pin
- sliding block
- fuel injection
- adjusting bolt
- 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
Links
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
- 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
Definitions
- the invention relates to a fuel injection pump according to the preamble of claim 1.
- the axial position of the control slide usually determines the start or end of spraying.
- the fuel injection quantity is controlled by the axial position of the control slide.
- an inaccurate axial position of the spool adversely affects the injection quality, which has a direct impact on the combustion, with the result that the engine runs out of round due to the injection not being timely or that it is too fast or too fast due to the imprecise metering quantity runs slowly.
- the adjusting bolt engages with a spherical head in the transverse groove of the control slide, so that there is a point contact between the head and the groove surfaces, which results in a long running time and high shaking load on these actuating elements premature wear and thus an undesired play between the head and the groove surfaces leads to the corresponding errors in the fuel control.
- the installation position of the adjustment bolt is determined during the adjustment because of the eccentric arrangement the head, the stroke position of the control spool is adjusted by turning the adjusting bolt and then countering it.
- the game resulting from wear and tear nullifies this adjustment, with the consequences already mentioned.
- the adjusting bolt is arranged in a rotationally fixed manner on a clamping ring serving as a fastening part, which clamps around the round torsion shaft.
- the required adjustment can be made relatively easily by rotating the clamp on the rotating shaft, but there is also the disadvantage mentioned above, in addition to other disadvantages, that the force transmission between adjusting bolts and associated surfaces of the transverse groove takes place in a punctiform manner, since the adjusting bolt is designed as a rotating part. Due to the only punctiform contact, there is correspondingly rapid and severe wear on the adjusting bolt and on the associated groove surfaces.
- the fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that the wear due to the line contact between the slide shoe and transverse groove surface is significantly less, so that not only a longer life of these transmission elements can be achieved, but also a much better quality of fuel control.
- the slide shoe is secured against axial displacement on the pin, which can advantageously be done according to one of claims 3, 4 or 5 by a pin arranged parallel to the contact surfaces of the slide shoe in the slide shoe, which in a Pin arranged annular groove or cross hole or tangential transverse groove engages.
- FIG. 1 shows a vertical section through a fuel injection pump according to the invention
- FIG. 2 shows a view of the adjusting bolt on an enlarged scale
- FIG. 3 shows an end view of the adjusting bolt according to arrow III-III in FIG. 2, of the first exemplary embodiment
- FIGS. 4 and 5 show views corresponding to FIGS. 2 and 3, but for the second exemplary embodiment and with a variant shown in broken lines for securing the position of the sliding block.
- the fuel injection pump shown is a multi-cylinder pump, of which only one pump element is shown in the vertical section according to FIG. 1. So is in a housing 1 Inlet cylinder liner 2, in which a pump piston 3 is driven by a camshaft 6 with the interposition of a roller tappet 4 with roller 5 against the force of a spring 7 for its axial movement forming the working stroke. A recess 8 is provided in the cylinder liner 2, in which a control slide 9 is axially displaceable on the pump piston 3.
- the recess 8 of the cylinder liner 2 is connected to a suction chamber 10, in which a rotating shaft 12 is arranged, through which the individual control slides 9, only one of which is shown, are axially displaced.
- a rotating shaft 12 In cross bores 41 of the rotating shaft 12 there are radially protruding adjusting bolts 14 which engage in a transverse groove 13 of the control slide 9, of which only one is also shown, which is fixed in its position on the rotating shaft 12 by means of a clamping nut 15 serving as a fastening part.
- a plug 16 is provided in the housing 1 opposite each of these clamping nuts 15, after removal of which an adjustment of the individual adjusting bolts 14 is possible by first loosening the clamping nut 15, then turning the adjusting bolt 14 for the adjustment, and then by the clamping nut 15 to be committed again.
- the individual control slides 9 of the injection pump can be coordinated with one another in their axial position, since in the first exemplary embodiment the adjusting bolts 14 are eccentric bolts, as explained in more detail below.
- These oblique grooves 24 interact with radial bores 25 of the control slide 9 in that they are opened by these radial bores 25 after a certain stroke of the pump piston 3.
- a guide pin 26 is inserted into a fitting groove 11 provided in the surface area of the cylinder liner 2, which leads into a longitudinal groove 27 of the control slide 9 engages.
- the pump piston 3 has a flattened portion on its lower section. 23 on which a driving member 31, which can be rotated by a control rod 29 in a known manner, engages, so that an axial displacement of the control rod 29 causes a rotation of the pump piston 3 and thus a change in the assignment of the oblique grooves 24 to the radial bores 25.
- a suction bore 32 is provided, which is exposed by the pump piston 3 in its bottom dead center position (as shown in the drawing).
- the fuel supply to the individual pump elements takes place via an inflow channel 33.
- the fuel not being injected flows out of the recesses 8 into the suction duct 10 and from there via a drain, not shown, into a return line and to the fuel tank or a feed pump of the injection pump, also not shown.
- the cylinder liner 2 has a flange 34 with which it is clamped to the housing 1 by bolts 35 and nuts 36.
- the common plane passing through the central axes of the bolts 35 is about 30 ° from the section plane through the housing 1 in Figure 1 twisted.
- the bolts 35 engage in bores which are no longer shown here and which are provided in the area between two pump elements in relation to the longitudinal extent of the pump in the pump housing 1.
- the adjusting bolt 14 is shown in an enlarged view.
- This adjusting bolt 14 has a pin 37, which is arranged eccentrically on a cheek 38, which in turn extends coaxially to a bearing section 39 which is fitted into one of the transverse bores 41 of the rotating shaft 12.
- a threaded portion 42 is provided on this adjusting bolt 14, which carries the clamping nut 15, so that when the clamping nut 15 is screwed tight, the cheek 38 is clamped onto the rotating shaft 12 in such a way that this adjusting bolt 14 is prevented from rotating in the rotating shaft 12.
- the eccentric pin 37 has a cylindrical outer surface 43, on which a slide shoe 44 is inserted by means of a central bore 40.
- This slide shoe 44 is secured against axial displacement by a pin 45, this pin 45 engaging in an annular groove 46 of the pin 37. Rotation of the slide shoe 44 on the pin 37 is thus possible.
- the pin 45 is fastened parallel to the contact surfaces 51 and tangentially to the wall of the central bore 40 of the slide shoe 44 or to the cylindrical outer surface 43 of the pin 37 in the slide shoe 44.
- the ends 47 of the pin 45 protrude beyond the side surfaces 48 of the slide shoe 44 and are angled to prevent the pin 45 from falling out.
- the surfaces 51 of the sliding shoe 44 which cooperate with the working surfaces 49 of the groove 13 are curved so that a cylindrical cross section of the sliding shoe 44 with flattened end faces 50 is formed (FIG. 2) and a linear contact between the working surfaces 49 and the surfaces also referred to as contact surfaces Surfaces 51 is guaranteed.
- the fuel injection pump shown in Figures 1 to 3 works as follows: During at least part of the suction stroke of the pump piston 3 and in the region of the bottom dead center of its stroke movement flows out of the suction chamber 10 via the oblique grooves 24, the transverse bore 23 and the blind bore 22 and the suction bore 32 fuel into the pump work chamber 18. In the subsequent pressure stroke of the pump piston 3 caused by camshaft 6, roller 5 and roller tappet 4, the pressure required for the injection builds up in the pump work chamber 18 only when these inflow channels between the suction chamber 10 and the Pump work space 18 are locked. As long as fuel flows back out of the pump work space 18 via these channels back into the suction space 10.
- the high pressure required for the injection builds up in the pump work space 18, and delivery to the internal combustion engine begins with the injection.
- the pump work chamber 18 is connected to the suction chamber 10, in that the oblique grooves 24 overlap with the radial bores 25, so that the fuel which is conveyed on is driven off under high pressure.
- This effective injection stroke of the pump piston 3 depends on its rotational position, which is determined by the control rod 29. Depending on the rotational position, the distance of the oblique grooves 24 from the radial bores 25 determined thereby is different, which corresponds to an injection stroke of different lengths.
- the axial position of the control slide 9, determines the beginning of the high-pressure injection with respect to the rotational position of the camshaft 6.
- the second embodiment shown in Figures 4 and 5 with a dash-dotted design variant differs essentially from the previously described first embodiment in a changed, only a limited rotatability of the position of the shoe and by the differently designed, non-rotatable by means of a mounting bracket on the Twist shaft mounted adjustment bolt.
- the same parts are provided with the same reference symbols, different parts with a reference symbol increased by 100 and new parts with new reference symbols.
- the adjusting bolt 114 of the second exemplary embodiment like the adjusting bolt 14 of the first exemplary embodiment, carries the cylindrical pin 137 which carries the sliding shoe 144 at its end section which engages in the transverse groove 13 of the control slide 9.
- the adjusting bolt 114 is on a fastening part designed as a U-shaped bracket 115 attached and z. B. fixed by brazing in its position.
- the transverse bore 52 in the pin 137 which is arranged parallel to the contact surfaces 51 in the sliding shoe 144 and is inserted through a transverse bore 52 crossing the longitudinal axis of the pin 137 Pin 45 provided.
- the position of the pin 45 is also fixed here by bending its free ends 47.
- the diameter of the transverse bore 52 is now chosen to be such a dimension larger than the diameter of the pin 45 that a twist play of the slide shoe 144 limited to a few degrees, preferably +/- 5 ° in both directions of rotation is possible.
- This limited backlash serves firstly to compensate for misalignments and thus prevents jamming and jamming of the components involved in controlling the position of the slide valve; and secondly, the slide shoe 144 is prevented from rotating away from its installation position provided for the actuation of the control slide 9 when the twist shaft 12 is inserted.
- a so-called "blind assembly” is possible, ie the slide shoes 144 mounted on the adjustment bolts 114 previously set in their installed position with respect to the rotating shaft 12 center automatically during assembly in the transverse grooves 13 of the control slide 9 receiving them, with the help of their arched contact surfaces 51 and the fact that they can only turn a few degrees from the final installation position.
- the aforementioned setting which is to be carried out outside the controller housing, of the installation position of the adjusting bolts 114, which is responsible for the correct stroke position of the control slide 9, is set by exchanging intermediate plates of different thicknesses between two opposing surfaces on the rotating shaft 12 and the fastening part 115, but is not the subject of the present case Invention.
- the pin 45 assumes the same position as in the first exemplary embodiment according to FIGS. 1 to 3.
- the pin 45 traverses the slide shoe 144 parallel to its contact surfaces 51 and tangentially to the wall of the central bore 40 in the slide shoe 144.
- the lateral surface 43 of the pin 137 on the adjusting bolt 114 has a rectified transverse groove 53, into which the pin 45 engages with a slight lateral but somewhat enlarged distance from the groove base 53a.
- This distance of the pin 45 to the groove base 53a is dimensioned such that the previously described twisting play of the sliding block 144, which is limited to a few angular degrees, is ensured.
- this securing of the position of the sliding shoe 144 allows the greatest possible reduction in the axial play while maintaining the torsional play.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE3610927 | 1986-03-24 | ||
DE3610927 | 1986-03-24 | ||
DE3707646 | 1987-03-10 | ||
DE19873707646 DE3707646A1 (de) | 1986-03-24 | 1987-03-10 | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0262167A1 true EP0262167A1 (fr) | 1988-04-06 |
EP0262167B1 EP0262167B1 (fr) | 1990-05-30 |
Family
ID=25842516
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP87901394A Expired - Lifetime EP0262167B1 (fr) | 1986-03-24 | 1987-03-19 | Pompe d'injection de carburant pour moteurs a combustion interne |
Country Status (5)
Country | Link |
---|---|
US (1) | US4850823A (fr) |
EP (1) | EP0262167B1 (fr) |
JP (1) | JPS63502914A (fr) |
DE (2) | DE3707646A1 (fr) |
WO (1) | WO1987005969A1 (fr) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3870748D1 (de) * | 1987-07-25 | 1992-06-11 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen. |
DE3736091A1 (de) * | 1987-10-24 | 1989-05-03 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
DE4041656A1 (de) * | 1990-12-22 | 1992-07-02 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
FI93985C (fi) * | 1991-04-17 | 1995-06-26 | Waertsilae Diesel Int | Polttoaineen ruiskutuspumpun asennus- ja kytkentäjärjestely |
JP2017173438A (ja) * | 2016-03-22 | 2017-09-28 | ヤマハ株式会社 | 楽器筐体用のピン組立体 |
JP6906620B2 (ja) * | 2017-03-09 | 2021-07-21 | ティロロン−シュルニッヒ ゲゼルシャフト エムベーハー | 把持機構用の支持装置及びカム制御軸 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2564830A (en) * | 1945-11-08 | 1951-08-21 | Bendix Aviat Corp | Fuel injection apparatus |
US2905020A (en) * | 1955-02-24 | 1959-09-22 | Kloeckner Humboldt Deutz Ag | Device for use in connection with fuel injection pumps for adjusting the delivery thereof |
DE1526725C3 (de) * | 1966-08-01 | 1973-10-25 | L'orange Kg, 7000 Stuttgart | Mehrzylinder Kraftstoffeinspntz pumpe |
US3385221A (en) * | 1967-03-07 | 1968-05-28 | Caterpillar Tractor Co | Multi-plunger engine fuel oil pump |
AU563901B2 (en) * | 1984-05-08 | 1987-07-23 | Bosch Automotive Systems Corporation | Fuel injection pump and method of adjusting the same pump |
JPS6114743U (ja) * | 1984-06-29 | 1986-01-28 | 株式会社ボッシュオートモーティブ システム | 燃料噴射装置 |
DE3435987A1 (de) * | 1984-10-01 | 1986-04-10 | Robert Bosch Gmbh, 7000 Stuttgart | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
JPS61123756A (ja) * | 1984-11-16 | 1986-06-11 | Diesel Kiki Co Ltd | 燃料噴射ポンプ |
DE3522451A1 (de) * | 1985-06-22 | 1987-01-02 | Bosch Gmbh Robert | Kraftstoffeinspritzpumpe fuer brennkraftmaschinen |
-
1987
- 1987-03-10 DE DE19873707646 patent/DE3707646A1/de not_active Withdrawn
- 1987-03-19 DE DE8787901394T patent/DE3762985D1/de not_active Expired - Lifetime
- 1987-03-19 US US07/135,157 patent/US4850823A/en not_active Expired - Fee Related
- 1987-03-19 JP JP62501859A patent/JPS63502914A/ja active Pending
- 1987-03-19 WO PCT/DE1987/000114 patent/WO1987005969A1/fr active IP Right Grant
- 1987-03-19 EP EP87901394A patent/EP0262167B1/fr not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO8705969A1 * |
Also Published As
Publication number | Publication date |
---|---|
US4850823A (en) | 1989-07-25 |
JPS63502914A (ja) | 1988-10-27 |
WO1987005969A1 (fr) | 1987-10-08 |
EP0262167B1 (fr) | 1990-05-30 |
DE3707646A1 (de) | 1987-10-08 |
DE3762985D1 (de) | 1990-07-05 |
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