EP0261102A1 - Pompe à combustible pour moteur à injection et son procédé de fabrication - Google Patents

Pompe à combustible pour moteur à injection et son procédé de fabrication Download PDF

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Publication number
EP0261102A1
EP0261102A1 EP87890211A EP87890211A EP0261102A1 EP 0261102 A1 EP0261102 A1 EP 0261102A1 EP 87890211 A EP87890211 A EP 87890211A EP 87890211 A EP87890211 A EP 87890211A EP 0261102 A1 EP0261102 A1 EP 0261102A1
Authority
EP
European Patent Office
Prior art keywords
pump piston
pump
piston liner
intermediate piece
liner
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
EP87890211A
Other languages
German (de)
English (en)
Other versions
EP0261102B1 (fr
Inventor
Theodor Dipl.-Ing. Dr. Stipek
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 AG
Robert Bosch GmbH
Original Assignee
Robert Bosch AG
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 AG, Robert Bosch GmbH filed Critical Robert Bosch AG
Publication of EP0261102A1 publication Critical patent/EP0261102A1/fr
Application granted granted Critical
Publication of EP0261102B1 publication Critical patent/EP0261102B1/fr
Expired 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
    • F02M59/44—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
    • F02M59/48—Assembling; Disassembling; Replacing
    • F02M59/485—Means for fixing delivery valve casing and barrel to each other or to pump casing

Definitions

  • the invention relates to a fuel injection pump for injection internal combustion engines with at least one pump element, in which an intermediate piece having the delivery channel for the fuel delivered by the pump piston and optionally the pressure valve seat is pressed sealingly against the pump piston sleeve by means of the pressure valve housing, the front end of the pump piston sleeve and the intermediate piece have perpendicular, mutually cooperating sealing surfaces standing perpendicular to the pump piston liner axis or the intermediate piece has a hollow conical support surface which is coaxial with the pump piston liner and is designed as a sealing surface, against which a conical surface of the pump piston liner which is coaxial with the pump piston liner is supported, and to a method for producing such a fuel injection pump.
  • the pump piston liner In fuel injection pumps, the pump piston liner usually has a flat end face, which is pressed against the intermediate piece in a sealing manner by tension.
  • the end faces of the pump piston liner and intermediate piece are finely ground, polished or lapped, so that the end faces pressed against one another themselves form the seal.
  • Such a design is chosen in particular when high injection pressures of, for example, 1500 bar are considered.
  • the pump piston liner has an inner diameter which is larger than the diameter of the delivery channel in the intermediate piece.
  • the high delivery pressure therefore has an effect on the pump piston liner in the sense of widening the same, while the solid intermediate piece is not or hardly deformed by the fuel pressure. There are therefore slight movements between the sealing surface of the pump piston liner and the sealing surface of the intermediate piece, and these microscopic movements lead to the formation of friction rust, which impairs the sealing effect.
  • An injection pump has become known from AT-PS 312 993, in which either flat or conical sealing surfaces are provided between the piston sleeve and the pressure valve housing.
  • a disadvantage of a design with conical sealing surfaces is that the contact and spreading forces in the cone are dependent on the tightening torque of the screw connection, which is subject to great tolerances, which makes it difficult to accurately measure the forces required for proper sealing function.
  • the object of the invention is to avoid the formation of friction rust on the sealing surfaces between the pump piston liner and the intermediate piece without increasing the dead working space of the pump element. Furthermore, the invention aims to provide a good seal between the piston liner and the pressure valve support and, at the same time, to enable the piston liner to be supported against excessive radial expansion under the internal pressure.
  • the invention consists essentially in the fact that both a hollow-cone-shaped support surface of the intermediate piece and a conical surface of the pump piston sleeve as well as flat sealing surfaces perpendicular to the pump piston axis are provided, which are dimensioned such that, in the non-clamped state, a gap between the flat sealing surfaces lying perpendicular to the pump piston sleeve axis consists. Since the pump piston liner is supported radially at its front end against the intermediate piece via the conical surface, an expansion of the pump piston liner under the effect of the high delivery pressure is avoided.
  • Compliance with these limits is determined by dimensioning the width of the gap that occurs in the unloaded state between the flat sealing surfaces of the pump piston liner and the intermediate piece.
  • the formation of a gap between the flat sealing surfaces in the unclamped state further causes, after screwing, that in the conical sealing surface between the bush and the body there is a pressure defined within narrow limits even in the unloaded state, as a result of which a good seal with simultaneous support of the piston bush against too much radial expansion is achieved under the internal pressure.
  • the hollow-conical support surface of the intermediate piece and the conical surface of the pump piston liner are surrounded by the flat sealing surfaces of the intermediate piece and the pump piston liner perpendicular to the pump piston liner axis, which results in a very space-saving construction.
  • the conical surface of the pump piston liner is preferably formed on the outside of an annular rib surrounding the piston running surface of the pump piston liner, the inside of which merges into the bore of the pump piston liner.
  • the pump pressure which acts as an expansion, acts from the inside out. Due to the fact that this pump pressure is absorbed in the inner area of the pump piston sleeve by the conical support surfaces, an elastic deformation of the pump piston sleeve in the area of the flat sealing surfaces lying on a larger radius and thus also the slightest formation of fretting rust is avoided with certainty.
  • the hollow-conical support surface of the intermediate piece exerts a radially inward pressure on the ring rib having the conical surface.
  • the bore of the pump piston liner in the region of the annular rib is preferably widened to a larger diameter in a manner known per se. This expansion avoids the risk of the piston jamming in the pump piston liner by narrowing the running surface in the area of the annular rib.
  • the hollow-conical support surface and the conical surface of the pump piston liner are preferably shaped after cones with a very small cone angle of 5 ° to 20 °. This results in large axial clearances at the start of assembly that are easy to control. In addition, there is little or no axial force between the bush and the body because there is self-locking.
  • the cone angle of the cone according to which the conical surface of the pump piston sleeve is shaped, is expediently slightly smaller than the cone angle, according to which the hollow-conical support surface is shaped. If the conical surfaces themselves also act as sealing surfaces, this has the advantage that the sealing surfaces concentrate on a smaller area and therefore the sealing pressure increases.
  • the flat sealing surface perpendicular to the pump piston sleeve axis is expediently formed at least partially on an outwardly projecting annular flange provided on the end of the pump piston sleeve facing the intermediate piece, by means of which the pump piston sleeve is supported against the pump housing. So that the contact pressure is introduced directly into the injection pump housing, so that the rest of the pump piston liner is relieved.
  • the end faces of the intermediate piece and / or the pump piston liner can be excluded in an annular area between the hollow-conical support surface or the conical surface of the pump piston liner and the flat sealing surfaces lying perpendicular to the pump piston axis.
  • the manufacturing tolerances for the conical surfaces have a comparatively strong effect on the compliance with the width of the gap, which is to occur in the non-tightened state between the flat sealing surfaces, from, which makes it difficult to maintain the correct pressing forces between the conical surfaces and the flat sealing surfaces.
  • a method for producing an injection pump according to the invention therefore consists, according to the invention, in that the tapered surface and the flat sealing surface of one of the parts to be pressed together (pump piston liner and intermediate piece) are finished in the toleranced nominal dimensions and the width of the pump piston liner in the uncompressed state and the intermediate piece of the resulting gap between the flat sealing surfaces of the pump piston liner and the intermediate piece is set by finishing the tapered surface (cone or hollow cone) of the other part (intermediate piece or pump piston liner) in accordance with the actual dimensions of the finished part.
  • FIG. 1 shows an axial section through a pump element of an injection pump and the pump housing.
  • Fig. 2 and 3 show different variants in partial axial sections.
  • 1 represents the pump housing, 2 the pump piston sleeve inserted into this, 3 the pump piston and 4 the working chamber of the pump piston 3.
  • 5 is the pressure valve and 6 is the delivery channel for the fuel pressurized in the working chamber 4.
  • 7 is an intermediate piece, which is pressed against the pump piston liner 2 by means of screws 9 acting on the pump housing 1 by means of the pressure valve housing 8.
  • the pump piston liner 2 is designed with an annular rim 10 which has a conical surface 11 on its outside.
  • the intermediate piece has a hollow conical surface 12 against which the conical surface 11 is supported radially. In this way, an expansion of the sleeve under the fuel pressure in the working space 4 of the pump piston 3 is avoided, this conical surface 11, together with the hollow conical surface 12, also providing a seal.
  • the hollow-conical sealing surface 12 of the intermediate piece 7 and the conical surface 11 of the pump piston liner 2 are surrounded by flat sealing surfaces which are perpendicular to the axis of the pump piston liner 2, the flat sealing surface of the intermediate piece 7 being designated by 13 and the flat sealing surface of the pump piston liner 2 by 14. Between these flat sealing surfaces 13, 14 and the conical surfaces 11, 12, the intermediate piece 7 and the pump piston liner 2 have recesses 15, so that the flat sealing surfaces 13, 14 are limited to narrow ring surfaces.
  • the hollow conical surface 12 of the intermediate piece 7 and the conical surface 11 of the pump piston liner 2 have cone angles ⁇ , which are small and are, for example, 5 to 20 °.
  • the planar sealing surfaces 13, 14 and the conical surfaces 11 and 12 are dimensioned such that, when clamped together, a gap 16 remains between the flat sealing surfaces 13, 14, which is reduced to zero by clamping the intermediate piece 7 with the pump piston liner 2, so that the flat sealing surfaces are pressed together with a certain force.
  • This gap 16 which exists in the non-clamped state, determines the extent of the pressure of the conical surface 11 against the hollow conical surface 12 in the clamped state. This also results in a radially inward force acting on the annular rib 10.
  • an exemption 17 formed by a recess is provided in this area.
  • the intermediate piece 7 has an annular rib 18 which engages in an annular groove 19 in the pump piston liner 2.
  • the hollow conical surface 12 is formed on the annular rib 18 and the conical surface 11 on the wall of the annular groove 19.
  • FIG. 3 differs from the embodiment of Figure 1 in that the flat sealing surface 14 is partially formed on an annular flange 20 of the pump piston liner 2, which is supported against an inwardly projecting ring rim 21 of the injection pump housing 22. The clamping forces are introduced into the pump housing 22 through this ring flange 20 and the ring flange 21.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP19870890211 1986-09-10 1987-09-10 Pompe à combustible pour moteur à injection et son procédé de fabrication Expired EP0261102B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT2441/86 1986-09-10
AT244186 1986-09-10

Publications (2)

Publication Number Publication Date
EP0261102A1 true EP0261102A1 (fr) 1988-03-23
EP0261102B1 EP0261102B1 (fr) 1989-10-11

Family

ID=3534411

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19870890211 Expired EP0261102B1 (fr) 1986-09-10 1987-09-10 Pompe à combustible pour moteur à injection et son procédé de fabrication

Country Status (2)

Country Link
EP (1) EP0261102B1 (fr)
DE (1) DE3760755D1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2278163A1 (fr) * 2009-07-20 2011-01-26 Delphi Technologies Holding S.à.r.l. Ensemble de pompe
WO2015052083A1 (fr) * 2013-10-08 2015-04-16 Robert Bosch Gmbh Pompe, en particulier pompe haute pression à carburant
IT201600071714A1 (it) * 2016-07-08 2018-01-08 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna
CN111790907A (zh) * 2020-08-18 2020-10-20 包头永真静平磁性材料科技有限公司 一种用于钕铁硼生产的冷等静压设备

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB486378A (en) * 1937-08-31 1938-06-02 Rudolf L Orange Improvements in fuel injection pumps for internal combustion engines
DE1910169A1 (de) * 1968-03-01 1969-10-02 Bryce Berger Ltd Kraftstoff-Einspritzpumpe
DE2135905A1 (de) * 1971-07-17 1973-01-25 Kloeckner Humboldt Deutz Ag Brennstoffeinspritzpumpe
AT312993B (de) * 1972-01-27 1974-01-25 Friedmann & Maier Ag Einspritzpumpe
FR2305602A1 (fr) * 1975-03-27 1976-10-22 Vysoke Uceni Technicke Rektora Pompe d'injection pour moteurs diesel, notamment pour moteurs a pressions d'injection elevees
AT338049B (de) * 1975-06-27 1977-07-25 Friedmann & Maier Ag Brennstoffeinspritzpumpe fur einspritzbrennkraftmaschinen

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB486378A (en) * 1937-08-31 1938-06-02 Rudolf L Orange Improvements in fuel injection pumps for internal combustion engines
DE1910169A1 (de) * 1968-03-01 1969-10-02 Bryce Berger Ltd Kraftstoff-Einspritzpumpe
DE2135905A1 (de) * 1971-07-17 1973-01-25 Kloeckner Humboldt Deutz Ag Brennstoffeinspritzpumpe
AT312993B (de) * 1972-01-27 1974-01-25 Friedmann & Maier Ag Einspritzpumpe
FR2305602A1 (fr) * 1975-03-27 1976-10-22 Vysoke Uceni Technicke Rektora Pompe d'injection pour moteurs diesel, notamment pour moteurs a pressions d'injection elevees
AT338049B (de) * 1975-06-27 1977-07-25 Friedmann & Maier Ag Brennstoffeinspritzpumpe fur einspritzbrennkraftmaschinen

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, Band 7, Nr. 269 (M-259)[1414], 30. November 1983; & JP-A-58 148 268 (DIESEL KIKI K.K.) 03.09.1983 *

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2278163A1 (fr) * 2009-07-20 2011-01-26 Delphi Technologies Holding S.à.r.l. Ensemble de pompe
WO2011009839A1 (fr) * 2009-07-20 2011-01-27 Delphi Technologies Holding S.À.R.L. Ensemble pompe
CN102575667A (zh) * 2009-07-20 2012-07-11 德尔福技术控股有限公司 泵组件
US9518546B2 (en) 2009-07-20 2016-12-13 Delphi International Operations Luxembourg S.A.R.L. Pump assembly
WO2015052083A1 (fr) * 2013-10-08 2015-04-16 Robert Bosch Gmbh Pompe, en particulier pompe haute pression à carburant
IT201600071714A1 (it) * 2016-07-08 2018-01-08 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna
CN111790907A (zh) * 2020-08-18 2020-10-20 包头永真静平磁性材料科技有限公司 一种用于钕铁硼生产的冷等静压设备

Also Published As

Publication number Publication date
DE3760755D1 (en) 1989-11-16
EP0261102B1 (fr) 1989-10-11

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