WO1989010479A1 - Unite de cylindre et piston a haute pression - Google Patents

Unite de cylindre et piston a haute pression Download PDF

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Publication number
WO1989010479A1
WO1989010479A1 PCT/EP1989/000424 EP8900424W WO8910479A1 WO 1989010479 A1 WO1989010479 A1 WO 1989010479A1 EP 8900424 W EP8900424 W EP 8900424W WO 8910479 A1 WO8910479 A1 WO 8910479A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
pressure
cylinder
diameter
grooves
Prior art date
Application number
PCT/EP1989/000424
Other languages
German (de)
English (en)
Inventor
Jacob Heidemans
Original Assignee
Hei-Tech B.V.
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
Priority claimed from NL8801046A external-priority patent/NL8801046A/nl
Priority claimed from NL8801479A external-priority patent/NL8801479A/nl
Priority claimed from NL8802183A external-priority patent/NL8802183A/nl
Application filed by Hei-Tech B.V. filed Critical Hei-Tech B.V.
Publication of WO1989010479A1 publication Critical patent/WO1989010479A1/fr

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
    • 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
    • F02M59/265—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 characterised by the arrangement or form of spill port of spill contour on the 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
    • F02M59/44—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
    • F02M59/442—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 means preventing fuel leakage around pump plunger, e.g. fluid barriers
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil

Definitions

  • the invention relates to piston-cylinder unit high pressure 'a is movably guided piston having a free end whose transverse to the lateral surface of the piston end face of a movable wall formed with a cylinder and a high pressure chamber in the Zy ⁇ relieving a.
  • Such a high-pressure piston-cylinder unit can be found as a high-pressure pump, such as. B. as an injection pump of a diesel engine.
  • the object of the invention is to provide a high-pressure piston-cylinder unit of the generic type which can also be used at very high pressures without the risk of seizing.
  • the object is achieved in that the boundary gap between the piston outer surface and the cylindrical surface has one or more limited sections in which he ines to achieve e "pressure compensation is extended over the circumference.
  • This proposed solution is based on the consideration that the seizure of the piston at very high working pressures is due to the fact that the free end of the piston within the cylinder can in principle assume a position that is not concentric even with tight tolerances to the cylinder wall. As soon as the piston takes up such a non-concentric position, the high pressure will most strongly propagate into the area between the piston skirt and the cylinder, in which the gap between the piston skirt and the cylinder is greatest. This increases the eccentric position of the piston. This ultimately results in the piston being pressed against the cylinder wall at high pressure.
  • the limit gap is widened by decreasing the piston diameter in the region of the high-pressure end face in the direction of this end face.
  • the high pressure of the high-pressure chamber acts uniformly over the circumference of the piston in the area with the decreasing diameter and thus exerts a centering effect.
  • the decrease in the piston diameter can be realized in such a way that the outer surface of the piston is conical in the area of the decreasing diameter.
  • it can also be designed stepped in the longitudinal cross section. If, during operation of the piston-cylinder unit, an eccentric position of the piston is established in the cylinder, the pressure on the side with the greater play can partially "escape" downwards due to a pressure drop in the limit gap.
  • the resulting pressure in the jacket area decreases with the decreasing diameter.
  • the dimensioning of the jacket area with the decreasing diameter which depends, among other things, on the viscosity of the pressure medium, can be determined for the respective embodiment using methods known for this purpose and possibly additionally by means of a corresponding test.
  • the smallest diameter must in any case be designed so that the piston in the cylinder can never come into contact with the cylinder even in an unfavorable position. Any contact may only be made at a certain distance from this smallest diameter, namely where the piston has the nominal diameter again.
  • a preferred embodiment of the first basic embodiment of the invention is described in claim 5.
  • the arrangement of a guide head increases the effect of the mechanism on which the invention is based and thus achieves secure centering.
  • a reduction in the piston diameter can be provided in the region of the remaining end face of the piston, which has the shape of a pressure edge due to the arrangement of the guide head, so that the above-described effect of the design according to the invention is retained at this point .
  • the axial length of the jacket area with the decreasing diameter is at least as large as 1/5 of the nominal diameter of the piston-cylinder unit.
  • the reduction in diameter of the piston should preferably have values in the range from 4 ⁇ m to 50 ⁇ m, although in special cases even larger diameter reductions can lead to success.
  • the invention is advantageous in the case of injection pumps for internal combustion engines, in particular large diesel engines, in which case the 1
  • the piston diameter decreases in the direction of the high-pressure pressure edge in the area of the pressure edge of the piston.
  • a second basic embodiment of the invention is characterized in 5 that the extension of the marginal gap between the lateral surface of piston-and-cylinder surface is carried out by one or a plurality of spaced circumferential grooves in the outer surface of the piston and / or in the cylindrical surface.
  • a third basic embodiment of the invention is characterized in that the expansion of the boundary gap between the piston surface and the cylinder surface by at least two arranged centrally symmetrically with respect to the central axis of the piston-cylinder unit and at least over a part of the stroke with the vertical
  • This design according to the invention in turn has the effect of keeping the pressure difference low when the piston is eccentrically in the cylinder, in order to avoid excessive eccentric forces of the piston jacket 30 on the cylinder wall.
  • the grooves should run axially and be so long that they are connected to the high-pressure chamber during the entire stroke stand fertilizer. In this way it is ensured that in the area of the limit gap adjacent to the grooves there is almost the same pressure as in the high pressure chamber, which results in a central guidance of the piston due to the central symmetrical arrangement of the grooves.
  • a further embodiment of the embodiment with centrally symmetrically arranged grooves is characterized in that the grooves are arranged in the region of the inlet and outlet openings of the cylinder and are curved, preferably circular or elliptical.
  • Each curved groove is advantageously self-contained, which has, among other things, manufacturing advantages.
  • the grooves should preferably have a depth of 5 to 50 ⁇ m, but in individual cases can also be even deeper.
  • the embodiment of the invention with grooves arranged centrally symmetrically is also advantageously suitable for use in injection pumps of internal combustion engines, in particular of diesel engines with an undercut piston skirt surface and an oblique control edge for volume control.
  • FIG. 1 shows a longitudinal section of a first basic embodiment of an inventive device 1 high-pressure piston-cylinder unit
  • Fig. 2 is a longitudinal section of a high pressure fuel injection pump for a diesel engine, the piston-cylinder unit with the 5 features of the invention acc. 1 is formed,
  • FIG. 3 shows a detail from the piston-cylinder unit of the fuel pump according to FIG. 2, enlarged and in perspective, in an alternative embodiment,
  • FIG. 4 shows a further alternative embodiment corresponding to FIG. 3, in which the pump piston is equipped with a guide head,
  • FIG. 6 shows an alternative embodiment corresponding to FIG. 5 with circumferential grooves in the cylinder surface
  • FIG. 7 shows a representation corresponding to FIG. 3 of the third embodiment of the invention with axially extending grooves in the cylinder surface
  • FIG. 8 shows an alternative embodiment to FIG. 7 with a wide groove in the cylinder surface
  • FIG. 9 shows a further alternative embodiment to FIG. 7 with curved grooves in the cylinder surface and in the 0:
  • the piston-cylinder unit shown in FIG. 1 is essentially a simplified section of the fuel pump according to FIG. 2, only the elements directly affected by the invention being shown for ease of understanding.
  • a pump piston 5 is guided in a high-pressure cylinder 2 and slides up and down during its pumping movement in accordance with the indicated double arrow, thereby opening or covering a fuel supply opening 18 in order to carry out a pressure stroke.
  • An outlet channel 21 * on the end face of the cylinder 2 is to be closed off by a high-pressure valve (not shown), which only pumps the medium, eg, high pressure, in the high-pressure chamber 3 of the piston-cylinder unit.
  • B. fuel can flow out of the high pressure chamber 3.
  • the end face 52 arranged transversely to the outer surface of the piston 5 thus forms a movable wall of the high pressure chamber 3.
  • the boundary gap is formed between the outer surface of the piston 5 and the cylindrical surface of the cylinder 2, which permits the sliding movement of the piston 5 in the cylinder 2.
  • this limit gap is now widened in the area 53 of the high-pressure surface 52 in the direction of this end surface 52 in that the piston diameter decreases, namely conically in the exemplary embodiment shown in FIG. 1.
  • the decrease in the diameter of the piston 5 in FIG. 1 is exaggerated for clarity. In reality, this decrease is so small, namely in the range of 5 to 50 ⁇ m, that it would not be recognizable from the drawing.
  • the high-pressure fuel pump shown in Fig. 2 is basically of conventional design, so that its description can be summarized.
  • the pump 1 consists of a cylinder 2 with a bore in the upper area, which forms the high pressure chamber 3.
  • a piston 5 is movably guided in this cylinder.
  • the piston 5 has a free end at the upper end, while a guide 17 is arranged at the lower end.
  • the piston 5 is driven and moves back and forth.
  • the Movement upwards is initiated by a plunger 10 which is driven, for example, by a cam arranged on the opposite side.
  • the downward movement is initiated by the spring 11.
  • the piston 5 is mounted in a known manner so that it can rotate about its longitudinal axis. To achieve this rotary movement of the piston 5, the latter is connected via the guide 57 to a rotatably mounted bushing 6, which is provided with a toothing 7. The toothing 7 engages in a rack 8 which is moved back and forth by means of the rod 9.
  • volume control is possible.
  • the fuel supply openings 18 remain closed for a certain period of the compression stroke.
  • the pressure drops. The pump function is ended.
  • the fuel is supplied by means of a fuel pump through a fuel line 41 on one side and discharged through line 42 on the other side, so that, apart from the fuel supply, cooling is achieved.
  • the actual movable pressure chamber wall of the high pressure chamber 3 is formed by the pressure edge 13.
  • the undercut area between this pressure edge and the control edge 14 is in constant communication with the high-pressure chamber 3.
  • the lateral surface 12 of the piston 5 bordering the pressure edge 13 now has a pressure surface in the direction of the pressure randes 13, ie in Fig. 2 decreasing in diameter upwards.
  • the outer surface 12 is conical, as in the example according to FIG. 1.
  • the outer surface 12 extends up to the nominal diameter of the piston 5.
  • a relief channel 16 emerges from the cylinder wall, so that any pressure build-up occurs is avoided in this area of the piston.
  • the piston 5 is centered in the cylinder by the conical outer surface 12. In the centered state, the high pressure has a uniform effect on the entire lateral surface 12.
  • the piston 5 In the area of the free upper end face 52 of the piston 5, the piston 5 also has a conical jacket area 15. This jacket area also has a centering effect, albeit less pronounced than that of the jacket area 12. In the area of the connecting channels 20 there is a the compression stroke, of course, a high pressure.
  • the design of a piston 5 shown in FIG. 3 has a piston jacket 26 which is stepped in the longitudinal cross-section in the region of the pressure edge 27.
  • the advantage of this embodiment is the simpler manufacture.
  • the high-pressure piston 5 is provided with a guide head 33 at its upper end.
  • This guide head 33 is through a piston section 32 with a smaller diameter with the Piston shaft connected.
  • a connection channel 35 is located between the end face 36 of the guide head 33 and the piston section 32.
  • the pumping function of the piston 5 basically corresponds to that of the piston 5 in FIG. 1.
  • the front shoulder 31 forms the actual delimitation of the high pressure chamber.
  • the guide head 33 has two on both sides . conical sections 37, 38 with a decreasing diameter in the diverging direction. Between these two conical sections 37 and 38, the guide head 33 has a reduced diameter, specifically to an axial length that corresponds at least to the stroke of the piston 5. In this area of the guide head 33, a channel 39 opens into the cylinder wall, which connects to the low-pressure area of the arrangement. The outlet opening of the channel 39 is always between the two conical disks 37 and 38. The centering effect corresponds to that which has already been described above, with the difference that the centering forces are twice as great.
  • the conical disks 37 and 38 point with the smallest diameter in the direction of the respective high-pressure side. In this case, the largest diameter bordering on the side of the nominal diameter of the piston is on the side with low pressure assigned to the outlet opening of the channel 39.
  • the pump piston is designated 126 because of the different design, while the cylinder, as in all exemplary embodiments, bears the reference number 2.
  • the piston 126 forms a pressure edge 127 as a high-pressure end face.
  • Three circumferential grooves 128 spaced apart from one another are arranged in the region of the lateral surface of the printing edge 127. The grooves level the pressure over the entire circumference. The lowest groove 128 can only become effective when the piston 126 has moved upwards during the compression stroke, so that the lowest groove 128 is located above the relief channel 129. Less than three circumferential grooves can also be arranged. In the embodiment according to FIG.
  • circumferential grooves 138 are located in the inner surface of the cylinder 2 and are positioned such that they come to lie between the pressure edge 137 of the piston 136 and the relief channel 139.
  • the effect of these grooves corresponds to that of the exemplary embodiment according to FIG. 5.
  • the widening of the boundary gap between the piston jacket surface and the cylinder surface is achieved by grooves arranged centrally symmetrically with respect to the central axis of the piston-cylinder unit.
  • these grooves are designated by 403 and run axially, they extend over such a length that they are connected to the high-pressure chamber 3 during the entire stroke path of the piston 5.
  • a connecting channel 20 in the piston 5, as shown in the exemplary embodiments according to FIGS. 2 to 6, can be omitted.
  • the grooves 403 result in a pressure in the boundary gap between the piston 5 and the cylinder 2 in the area between the grooves, between which there is no inlet or outlet opening, which is almost as large as the compression pressure in the high-pressure chamber 3.
  • pressure differences between one side of the piston with a larger gap and one side of the piston with a smaller gap can only be very small.
  • FIGS. 10a and 10b show the pressure curve in the boundary gap in each case in a previously known embodiment and in an embodiment in accordance with this invention. To clarify the principle, the situation is only shown in two dimensions, while the reality is three-dimensional.
  • four grooves 403 are arranged according to the invention, in which, since they are directly connected to the high-pressure chamber 3, the compression pressure also prevails. As a result, the pressure in the boundary gap between the grooves 403 is as high as the compression pressure.
  • Pressure drop occurs between the grooves 403 and the inlet and outlet channels 18.
  • the pressure difference between the one side of the piston and the other side of the piston is substantially smaller than in the previously known embodiment according to FIG . Fig. 10a.
  • FIG. 8 shows an embodiment in which two wide grooves 404 are arranged on the inside of the cylinder 2 instead of the four grooves 403 according to FIG. 7.
  • the grooves 404 each extend over a part of the cylinder circumference that is between 30 ° and 50 ⁇ .
  • FIG. 10 An embodiment is shown in FIG. 10, in which two self-contained grooves 405, 406 are arranged both in the area of the inlet channel 18 and in the area of the outlet channel, the grooves running in a circular manner, but each also having a different one
  • Form should be provided that they are arranged and formed centrally symmetrically with respect to the cylinder axis for the inlet channel 18 and the outlet channel.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

Une unité de cylindre et piston à haute pression comprend un cylindre (2) dans lequel se déplace un piston (5, 126, 136) et qui présente une extrémité libre dont la face frontale (52) transversale à l'enveloppe du piston (5, 126, 136) forme une paroi mobile d'une chambre de haute pression (3) dans le cylindre. L'écartement entre l'enveloppe du piston et la surface du cylindre présente une ou plusieurs sections limitées élargies qui assurent une répartition équilibrée de la pression autour de sa circonférence. L'élargissement dudit écartement peut être obtenu en réduisant le diamètre du pison au niveau de la face frontale ou en ménageant des rainures dans le piston ou dans la paroi du cylindre.
PCT/EP1989/000424 1988-04-22 1989-04-20 Unite de cylindre et piston a haute pression WO1989010479A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
NL8801046 1988-04-22
NL8801046A NL8801046A (nl) 1988-04-22 1988-04-22 Hoge druk plunjer-inrichting.
NL8801479A NL8801479A (nl) 1988-06-09 1988-06-09 Hoge druk plunjer-inrichting ii.
NL8801479 1988-06-09
NL8802183A NL8802183A (nl) 1988-09-05 1988-09-05 Hoge druk plunjer-inrichting iii.
NL8802183 1988-09-05

Publications (1)

Publication Number Publication Date
WO1989010479A1 true WO1989010479A1 (fr) 1989-11-02

Family

ID=27352203

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1989/000424 WO1989010479A1 (fr) 1988-04-22 1989-04-20 Unite de cylindre et piston a haute pression

Country Status (1)

Country Link
WO (1) WO1989010479A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2657652A1 (fr) * 1990-01-30 1991-08-02 Orange Gmbh Pompe a piston haute pression, notamment pour injection de gazole pour les moteurs diesel.
WO1999049209A1 (fr) * 1998-03-26 1999-09-30 Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh Unite cylindre-piston haute pression
EP1234975A2 (fr) 2001-02-26 2002-08-28 Wärtsilä Schweiz AG Unité cylindre-piston haute pression
WO2004088120A2 (fr) * 2003-04-01 2004-10-14 Avl List Gmbh Moteur a combustion interne
AT413865B (de) * 2003-04-01 2006-06-15 Avl List Gmbh Kolbeneinspritzpumpe zur kraftstoffförderung für brennkraftmaschinen
CN100436808C (zh) * 2003-04-01 2008-11-26 Avl里斯脱有限公司 一种驱动直接喷射式柴油机的方法和装置
WO2009083641A1 (fr) * 2008-01-02 2009-07-09 Wärtsilä Finland Oy Procédé et appareil permettant de tester le piston d'une pompe à injection
WO2015028195A1 (fr) * 2013-08-27 2015-03-05 Robert Bosch Gmbh Pompe à haute pression pour système d'injection de carburant ainsi que procédé de fabrication d'une pompe à haute pression pour système d'injection de carburant
DE102015016314A1 (de) * 2015-12-15 2017-06-22 L'orange Gmbh Kolbenpumpe

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH166315A (de) * 1932-11-17 1933-12-31 Bosch Robert Ag Einspritzpumpe für Brennkraftmaschinen mit stark wechselnder Drehzahl.
FR788642A (fr) * 1935-04-11 1935-10-14 Pompes d'injection de combustible
GB724986A (en) * 1953-04-02 1955-02-23 Crossley Premier Engines Ltd Improvements relating to fuel oil injection pumps of internal combustion engines
FR2198552A5 (fr) * 1972-08-31 1974-03-29 Bryce Berger Ltd
DE2741348A1 (de) * 1977-09-14 1979-03-15 Karl Kadletz Pumpe, insbesondere dosierpumpe
GB2077862A (en) * 1980-05-31 1981-12-23 Lucas Industries Ltd Fuel Pumping Apparatus
DE3332470A1 (de) * 1982-09-08 1984-03-08 Steyr-Daimler-Puch AG, 1011 Wien Kolbeneinspritzpumpe mit schraegkantensteuerung, insbesondere fuer dieselmotoren

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH166315A (de) * 1932-11-17 1933-12-31 Bosch Robert Ag Einspritzpumpe für Brennkraftmaschinen mit stark wechselnder Drehzahl.
FR788642A (fr) * 1935-04-11 1935-10-14 Pompes d'injection de combustible
GB724986A (en) * 1953-04-02 1955-02-23 Crossley Premier Engines Ltd Improvements relating to fuel oil injection pumps of internal combustion engines
FR2198552A5 (fr) * 1972-08-31 1974-03-29 Bryce Berger Ltd
DE2741348A1 (de) * 1977-09-14 1979-03-15 Karl Kadletz Pumpe, insbesondere dosierpumpe
GB2077862A (en) * 1980-05-31 1981-12-23 Lucas Industries Ltd Fuel Pumping Apparatus
DE3332470A1 (de) * 1982-09-08 1984-03-08 Steyr-Daimler-Puch AG, 1011 Wien Kolbeneinspritzpumpe mit schraegkantensteuerung, insbesondere fuer dieselmotoren

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2657652A1 (fr) * 1990-01-30 1991-08-02 Orange Gmbh Pompe a piston haute pression, notamment pour injection de gazole pour les moteurs diesel.
DE4002557A1 (de) * 1990-01-30 1991-08-08 Orange Gmbh Hochdruck-kolbenpumpe
WO1999049209A1 (fr) * 1998-03-26 1999-09-30 Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh Unite cylindre-piston haute pression
EP1234975A2 (fr) 2001-02-26 2002-08-28 Wärtsilä Schweiz AG Unité cylindre-piston haute pression
EP1234975A3 (fr) * 2001-02-26 2004-08-11 Wärtsilä Schweiz AG Unité cylindre-piston haute pression
KR100773437B1 (ko) * 2001-02-26 2007-11-05 베르트질레 슈바이츠 악티엔게젤샤프트 실린더 유닛 내의 고압 피스톤
WO2004088120A3 (fr) * 2003-04-01 2005-06-09 Avl List Gmbh Moteur a combustion interne
AT413865B (de) * 2003-04-01 2006-06-15 Avl List Gmbh Kolbeneinspritzpumpe zur kraftstoffförderung für brennkraftmaschinen
WO2004088120A2 (fr) * 2003-04-01 2004-10-14 Avl List Gmbh Moteur a combustion interne
CN100436808C (zh) * 2003-04-01 2008-11-26 Avl里斯脱有限公司 一种驱动直接喷射式柴油机的方法和装置
WO2009083641A1 (fr) * 2008-01-02 2009-07-09 Wärtsilä Finland Oy Procédé et appareil permettant de tester le piston d'une pompe à injection
US8220321B2 (en) 2008-01-02 2012-07-17 Wärtsilä Finland Oy Method and apparatus for testing the piston of an injection pump
WO2015028195A1 (fr) * 2013-08-27 2015-03-05 Robert Bosch Gmbh Pompe à haute pression pour système d'injection de carburant ainsi que procédé de fabrication d'une pompe à haute pression pour système d'injection de carburant
DE102015016314A1 (de) * 2015-12-15 2017-06-22 L'orange Gmbh Kolbenpumpe

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