EP0288669A1 - Pompe à injection de combustible pour moteur diesel - Google Patents
Pompe à injection de combustible pour moteur diesel Download PDFInfo
- Publication number
- EP0288669A1 EP0288669A1 EP88101862A EP88101862A EP0288669A1 EP 0288669 A1 EP0288669 A1 EP 0288669A1 EP 88101862 A EP88101862 A EP 88101862A EP 88101862 A EP88101862 A EP 88101862A EP 0288669 A1 EP0288669 A1 EP 0288669A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- pump piston
- piston
- regulating rod
- cylinder
- 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
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
- F04B49/121—Lost-motion device in the driving mechanism
-
- 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
- F02M59/28—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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/06—Control
Definitions
- the invention relates to a fuel injection pump for reciprocating internal combustion engines of the diesel type, with at least one pump piston which can be moved up and down in a cylinder and which has control edges in its lateral surface which extend obliquely to its longitudinal axis and which determine the start and end of delivery of the pump piston with holes in the cylinder, and with a device which pivots the pump piston about its longitudinal axis and which comprises a regulating rod which is mounted outside the cylinder and can be moved back and forth in a straight line and cooperates with the pump piston.
- the device pivoting the pump piston serves to change the amount of fuel to be injected into the working cylinder of the reciprocating piston internal combustion engine as a function of the load on the machine, by changing the position of the oblique control edges relative to the holes in the cylinder as a result of the pivoting that the start of delivery and / or the end of delivery of the pump piston shift.
- the size of the swivel range of the pump piston is limited due to the pump design and is approximately 60 °.
- the course of the oblique control edges in the lateral surface of the pump piston thus extends over the range of 60 °. Considered in the graphic development of the lateral surface, the oblique control edges are relatively steep.
- Such a steep course results in an unfavorable reproducibility of the injected fuel quantity, ie there is a relatively large deviation of the delivery stroke of the pump piston, that is to say the injection quantity, from the position of the regulating rod.
- Such deviations are caused, for example, by the sum of the inaccuracies in the transmission path from the controller engaging the regulating rod to the pump piston (play, tolerances, assembly inaccuracies, etc.).
- the steeper the control edge the greater the deviations in the piston stroke.
- Further disadvantages of the steep control edge course arise at the end of the injection phase in that the piston stroke becomes quite large, which is necessary to fully open the overflow hole in the cylinder through the associated control edge.
- Injection pumps of the type mentioned are also only used for constant injection start. It is practically impossible to advance the start of injection before the ignition TDC due to the steep control edge course.
- the invention has for its object to improve the injection pump of the type mentioned so that the disadvantages caused by the steep control edge course are avoided.
- the device has an adjusting sleeve which is arranged between the regulating rod and the pump piston, surrounds it eccentrically and is provided with an internal toothing and which engages with its internal toothing in an external toothing attached to the pump piston, and in that the adjusting sleeve is articulated with the regulating rod connected is.
- the larger swivel range of the pump piston now allows the course of the oblique control edges over a correspondingly larger circumference of the lateral surface of the To extend the pump piston, so that - seen in the drawing development - the control edges have a much smaller slope than before.
- the disadvantages described in connection with the steep control edge profile of the known injection pumps are thus considerably reduced.
- the deviations of the piston stroke due to the inaccuracies in the transmission path are therefore considerably smaller; the injection phase is ended more quickly because the piston stroke for the full opening of the overflow hole is reduced by the associated control edge.
- a pump cylinder 2 is provided in a pump housing 1, which is fixed in the pump housing 1 by a pump housing cover 3.
- a pump piston 4 is guided up and down, which is provided in its lateral surface near the upper piston end with control edges 5 which run obliquely to the longitudinal axis of the piston.
- control edges interact in a known manner with two radial bores (not shown in FIG. 1) in the wall of the pump cylinder 2, as a result of which the start of delivery and the end of delivery of the pump piston 4 are determined.
- the fuel to be injected is fed via an inlet line, also not shown in FIG.
- the pump piston 4 has at its lower end protruding from the pump cylinder 2 a flange 9 with which it rests on a pump tappet 10 which is guided in the pump housing 1 so as to be axially movable.
- the flange 9 is overlapped by a cap 11, which also surrounds part of the pump plunger 10 and on which the lower end of a compression spring 12 is supported.
- the upper end of the compression spring 12 is supported on a spring plate 13 which is fixed in the pump housing 1.
- a constant contact of the flange 9 on the pump tappet 10 is ensured by means of the compression spring 12.
- a roller 14 is rotatably mounted therein, which rolls on a cam 15 of a camshaft that drives the pump piston 4 in time with the diesel engine.
- the lower end of the pump cylinder 2 is surrounded by a sleeve 16, which at its lower end, which projects beyond the pump cylinder, is provided with two axial, diametrically opposite slots, into each of which a radial arm 17 of the pump piston 4 projects.
- the axial length of the slots is at least the same size as the maximum stroke of the pump piston 4.
- the sleeve 16 has in its area above the slots an external toothing 18 which is in engagement with an internal toothing 19 which is provided in an adjusting sleeve 20 arranged eccentrically to the sleeve 16 and thus to the pump piston 4.
- the Adjustment sleeve 20 is pivotally mounted in the pump housing 1 about its axis of rotation 21 (FIG. 3) and has a radially outwardly projecting stop tab 22 on its outer circumference. 1 is attached to the stop tab 22, which projects downward into a fork piece 24, which is adjustably fastened on a regulating rod 25 which can be moved back and forth transversely to the pump piston 4.
- the regulating rod 25 By moving the regulating rod 25 by the amount "s" (FIG. 2), the adjusting sleeve 20 can thus be pivoted through an angle of approximately 60 ° via the fork piece 24 and the driving pin 23, as is shown by the dash-dotted representation of the fork piece 24 and of the driving pin 23 is shown in Fig. 2. In the upper dash-dotted position in Fig.
- the lateral boundary surface 22 '(Fig. 3) of the stop tab 22 is on a stop screw 26 which is attached to the pump housing 1.
- the stop screw 26 is adjustable with the help of an adjusting nut 27.
- the same arrangement of the stop screw and the adjusting nut is located on the opposite side of the swivel range of the adjusting sleeve 20 and interacts with the boundary surface 22 ⁇ of the stop tab 22.
- the size of the path "s" and thus the size of the swivel range of the flap 22 is limited in that the housing 1 cannot be weakened further in the area mentioned.
- the pivoting movement of the adjusting sleeve 20 is translated into a larger adjusting movement of the sleeve 16 and thus of the pump piston 4.
- the size of the pivoting movement of the sleeve 16 depends on the size of the eccentricity "e" (FIG. 3) between the longitudinal axis of the pump piston and the axis 21 of the adjusting sleeve 20. It can be reach maximum swivel range of approximately 120 ° of the sleeve 16 or the pump piston 4.
- the lower half of the injection pump is inserted into an engine housing 30 in which the camshaft is also mounted. It is essential for the injection pump that the outer limit of the stop lug 22 lies within the diameter of the upper bore 31 in the engine housing that receives the pump housing 1, so that the injection pump can be easily installed and removed.
- an injection pump is arranged in the engine housing in the manner described and there is an associated cam corresponding to cam 15 on the common camshaft.
- the regulating rod 25 is also common to all working cylinders and has a fork piece 24 for each injection pump. By adjusting the fork pieces 24 relative to the regulating rod and adjusting the stop screws 26, the fuel quantities to be injected into the working cylinders can be made equal to one another.
- the sleeve 16 In a departure from the exemplary embodiment described, it is also possible to omit the sleeve 16 and to provide its external toothing directly on the pump piston 4. In such a case, the outer toothing would have to be longer in the axial direction so that it remains in engagement with the inner toothing 19 of the adjusting sleeve 20 during the up and down movement of the pump piston.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
- Jet Pumps And Other Pumps (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CH1652/87 | 1987-04-30 | ||
CH1652/87A CH672005A5 (fr) | 1987-04-30 | 1987-04-30 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0288669A1 true EP0288669A1 (fr) | 1988-11-02 |
EP0288669B1 EP0288669B1 (fr) | 1991-03-20 |
Family
ID=4215469
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP88101862A Expired - Lifetime EP0288669B1 (fr) | 1987-04-30 | 1988-02-09 | Pompe à injection de combustible pour moteur diesel |
Country Status (8)
Country | Link |
---|---|
EP (1) | EP0288669B1 (fr) |
JP (1) | JPS63272959A (fr) |
CH (1) | CH672005A5 (fr) |
DE (1) | DE3862056D1 (fr) |
DK (1) | DK164827C (fr) |
ES (1) | ES2022482B3 (fr) |
FI (1) | FI96535C (fr) |
NO (1) | NO168725C (fr) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2324124A (en) * | 1997-02-19 | 1998-10-14 | Caterpillar Inc | Injection rate shape device for a fill metered hydraulically actuated unit fuel injector |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103267012B (zh) * | 2013-05-29 | 2015-10-07 | 宁波合力机泵有限公司 | 一种改变柱塞容积的流量调节装置 |
JP7022380B2 (ja) * | 2018-01-31 | 2022-02-18 | いすゞ自動車株式会社 | 燃料ポンプ組付構造 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1054199A (fr) * | 1950-12-08 | 1954-02-09 | Daimler Benz Ag | Dispositif d'injection de carburant, en particulier avec pompe à injection et ajutage d'injection combinés en un bloc unitaire |
DE1910170A1 (de) * | 1968-03-01 | 1969-10-02 | Bryce Bereger Ltd | Kraftstoff-Einspritzpumpe |
US3498229A (en) * | 1967-11-01 | 1970-03-03 | Dake Corp | Hydraulic pump assembly |
EP0055245A2 (fr) * | 1980-12-18 | 1982-06-30 | Friedmann & Maier Aktiengesellschaft | Dispositif pour le positionnement et la coordination d'une pluralité de dispositifs d'injection |
DE3501287A1 (de) * | 1984-01-18 | 1985-07-25 | Friedmann & Maier AG, Hallein, Salzburg | Einspritzpumpe fuer einspritzbrennkraftmaschinen |
-
1987
- 1987-04-30 CH CH1652/87A patent/CH672005A5/de not_active IP Right Cessation
-
1988
- 1988-02-09 DE DE8888101862T patent/DE3862056D1/de not_active Expired - Fee Related
- 1988-02-09 EP EP88101862A patent/EP0288669B1/fr not_active Expired - Lifetime
- 1988-02-09 ES ES88101862T patent/ES2022482B3/es not_active Expired - Lifetime
- 1988-02-12 FI FI880655A patent/FI96535C/fi not_active IP Right Cessation
- 1988-03-11 DK DK134188A patent/DK164827C/da not_active IP Right Cessation
- 1988-04-12 JP JP63090152A patent/JPS63272959A/ja active Pending
- 1988-04-29 NO NO881890A patent/NO168725C/no unknown
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1054199A (fr) * | 1950-12-08 | 1954-02-09 | Daimler Benz Ag | Dispositif d'injection de carburant, en particulier avec pompe à injection et ajutage d'injection combinés en un bloc unitaire |
US3498229A (en) * | 1967-11-01 | 1970-03-03 | Dake Corp | Hydraulic pump assembly |
DE1910170A1 (de) * | 1968-03-01 | 1969-10-02 | Bryce Bereger Ltd | Kraftstoff-Einspritzpumpe |
EP0055245A2 (fr) * | 1980-12-18 | 1982-06-30 | Friedmann & Maier Aktiengesellschaft | Dispositif pour le positionnement et la coordination d'une pluralité de dispositifs d'injection |
DE3501287A1 (de) * | 1984-01-18 | 1985-07-25 | Friedmann & Maier AG, Hallein, Salzburg | Einspritzpumpe fuer einspritzbrennkraftmaschinen |
Non-Patent Citations (1)
Title |
---|
PATENT ABSTRACTS OF JAPAN, Band 9, Nr. 7 (M-350)[1730], 12. Januar 1985, Seite 153 M 350; & JP-A-59 158 372 (HINO JIDOSHA KOGYO K.K.) 07-09-1984 * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2324124A (en) * | 1997-02-19 | 1998-10-14 | Caterpillar Inc | Injection rate shape device for a fill metered hydraulically actuated unit fuel injector |
GB2324124B (en) * | 1997-02-19 | 2000-11-08 | Caterpillar Inc | Hydraulically-actuated fuel injection system |
Also Published As
Publication number | Publication date |
---|---|
FI880655A0 (fi) | 1988-02-12 |
DE3862056D1 (de) | 1991-04-25 |
FI96535C (fi) | 1996-07-10 |
CH672005A5 (fr) | 1989-10-13 |
DK164827C (da) | 1993-01-11 |
NO881890L (no) | 1988-10-31 |
ES2022482B3 (es) | 1991-12-01 |
NO881890D0 (no) | 1988-04-29 |
NO168725C (no) | 1992-03-25 |
DK134188D0 (da) | 1988-03-11 |
DK164827B (da) | 1992-08-24 |
DK134188A (da) | 1988-10-31 |
JPS63272959A (ja) | 1988-11-10 |
NO168725B (no) | 1991-12-16 |
FI96535B (fi) | 1996-03-29 |
FI880655A (fi) | 1988-10-31 |
EP0288669B1 (fr) | 1991-03-20 |
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