EP1489301B1 - Système d'entraînement pour une Pompe - Google Patents

Système d'entraînement pour une Pompe Download PDF

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Publication number
EP1489301B1
EP1489301B1 EP03253852A EP03253852A EP1489301B1 EP 1489301 B1 EP1489301 B1 EP 1489301B1 EP 03253852 A EP03253852 A EP 03253852A EP 03253852 A EP03253852 A EP 03253852A EP 1489301 B1 EP1489301 B1 EP 1489301B1
Authority
EP
European Patent Office
Prior art keywords
drive member
plunger
rider
drive
tappet
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.)
Expired - Lifetime
Application number
EP03253852A
Other languages
German (de)
English (en)
Other versions
EP1489301A1 (fr
Inventor
Todd Bordewyk
Ian R. Thornthwaite
Daniel J. Hopley
Detlev SCHÖPPE
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.)
Delphi Technologies Inc
Original Assignee
Delphi Technologies Inc
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 Delphi Technologies Inc filed Critical Delphi Technologies Inc
Priority to DE60309145T priority Critical patent/DE60309145T2/de
Priority to AT03253852T priority patent/ATE343060T1/de
Priority to EP03253852A priority patent/EP1489301B1/fr
Publication of EP1489301A1 publication Critical patent/EP1489301A1/fr
Application granted granted Critical
Publication of EP1489301B1 publication Critical patent/EP1489301B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F04B1/0404—Details or component parts
    • F04B1/0413—Cams
    • 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
    • F04B1/0404—Details or component parts
    • 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
    • F04B1/0404—Details or component parts
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam

Definitions

  • the invention relates to a drive arrangement for use in pump of the type suitable for use in a common rail fuel injection system of an internal combustion engine.
  • the invention relates to a drive arrangement for a pump having at least one pumping plunger that is driven by means of a drive member co-operating with a cam rider mounted upon the engine cam shaft.
  • each of the plungers is coupled to a respective drive member in the form of a tappet.
  • the cam carries a cam ring or cam rider that travels over the surface of the cam as it is driven by the engine.
  • Each tappet is located within a tappet bore provided in a main pump housing and is arranged so that, as the cam is driven, each tappet is caused to reciprocate within its respective bore, resulting in reciprocating motion to the plungers.
  • a base surface of the tappet is caused to translate laterally over a co-operating region of the rider surface.
  • the tappet is driven radially outward from the shaft, its respective plunger is driven to reduce the volume of the pump chamber. This part of the pumping cycle is referred to as the pumping stroke of the plunger, during which fuel within the associated pumping chamber is pressurised to a relatively high level.
  • US 6,077,056 which has at least one piston which is displaceably supported in a piston guide provided in a housing and therein defines a work chamber.
  • the piston is supported on a slide bearing face on a stroke ring which is rotatably supported on a crank element of a drive shaft so that the piston can be acted upon by the drive shaft.
  • a relief chamber is formed by a recess in a slide face on the piston and opens toward the slide bearing face on the stroke ring to communicate with the work chamber.
  • US 6,350,107 discloses a radial piston pump including a plurality of pistons disposed in a respective cylinder chamber, each having a plate connected to one end. A centre of each of the plates has a recess so that the stresses that occur in this location during operation are reduced.
  • a drive arrangement for a pumping plunger of a pump assembly comprising;
  • variable return loading of the drive member arises due to the hydraulic load exerted on the drive member by fuel within the pump chamber, the pressure of which increases and decreases throughout a pumping cycle, and that the maximum return load applied to the drive member occurs part way between BDC and TDC when fuel within the pump chamber is pressurised to its maximum value, just prior to associated outlet or delivery valve means of the pump chamber being opened to permit high pressure fuel delivery.
  • the invention provides the advantage that lubrication between the drive member and the cam rider is improved during the plunger pumping stroke.
  • the "squeeze film effect" which is provided as fluid within the variable volume is dispelled through said restricted flow means, is prolonged, to ensure a transient fluid pressure condition exists to support return loading of the drive member during that part of the pumping cycle when it is a maximum. Transient fluid pressure within the variable volume therefore supports return loading of the drive member for a longer period of duration than is provided by known drive arrangements of similar type.
  • the transient fluid pressure condition occurs part way between bottom-dead-centre (BDC) and top-dead-centre (TDC) of the pumping stroke.
  • BDC bottom-dead-centre
  • TDC top-dead-centre
  • the drive arrangement may be incorporated within a pump assembly of the type having three plungers, wherein the plungers are radially spaced around a cam rider which is common to all three plungers, this being a so-called radial fuel pump.
  • At least one of the drive member and the rider is shaped to define a recessed surface to define, together with a surface of the other of the drive member and the rider, said variable fluid volume.
  • the surface of the drive member may be shaped so as to be substantially concave.
  • the cam rider may include a substantially flattened surface which defines, together with the concave surface of the drive member, the variable fluid volume.
  • the cam rider may include a substantially concave surface which defines, together with the surface of the drive member, the variable fluid volume.
  • the drive member may be shaped to include a drive member side wall of annular form defining an annular surface that is co-operable with the surface of the rider to define the restricted flow means.
  • the drive member may be provided with a recessed surface of substantially U-shaped cross section.
  • the drive member may be shaped to define a radiussed surface to define the restricted flow means with the surface of the rider. This provides the benefit that lubricating fluid is encouraged to flow into the variable fluid volume during the return stroke of the drive member, and also in some configurations provides the benefit that the surface contact area between the drive member and the cam rider is increased, thereby reducing contact stresses.
  • a drive arrangement for a pumping plunger of a pump assembly comprises:
  • a pump assembly including a plunger and a drive arrangement for the plunger as claimed in the accompanying claim set.
  • the drive member takes the form of a tappet, for example a bucket tappet of substantially U-shaped cross-section.
  • the present invention relates to drive arrangement for a pump assembly, generally of the type shown in Figure 1.
  • the pump assembly 10 includes a first housing part 12 in the form of a main pump housing provided with an axially extending opening through which a cam drive shaft extends when the assembly 10 is installed within the engine.
  • a cam drive shaft extends when the assembly 10 is installed within the engine.
  • the central axis 16 of the drive shaft is identified, although the drive shaft itself is not visible.
  • the drive shaft co-operates with a drive arrangement which includes an eccentrically mounted cam 18 carrying cam ring or rider 20 having a generally circular-like cross section.
  • first, second and third pump heads or units Mounted around the cam 18 are first, second and third pump heads or units, generally referred to as 22a, 22b, 22c. Each pump unit is identical and so only one will be described in detail.
  • the first pump head 22a includes a plunger 24 which is reciprocal within a plunger bore 26 to cause pressurisation of fuel within a pump chamber 28 defined at a blind end of the bore 26.
  • Fuel at relatively low pressure is supplied to the pump chamber 28, in use, and is pressurised to a high level suitable for injection as the plunger 24 is driven to perform a pumping stroke, that is between bottom-dead-centre (BDC) and top-dead-centre (TDC).
  • FIG 2 shows a first embodiment of a drive arrangement for the pump assembly in Figure 1.
  • the plunger has an associated a drive member 30 in the form of a tappet is co-operable with the plunger 24.
  • the tappet 30 may be a bucket tappet, of generally U-shaped or channelled cross section, and includes a base 32 and first and second side walls 34.
  • the upper surface of the tappet base 32 may be provided with recess (not shown) for locating one end of a plunger return spring (item 36 - Figure 1), mounted concentrically with the plunger 24, which serves to drive a plunger return stroke between TDC and BDC.
  • a circlip (not shown) couples the return spring 36 to the plunger 24 at its lower end.
  • a lower surface 37 of the tappet base 32 is co-operable with a flattened surface region 38, or flat, of the rider 20.
  • the generally circular cam rider 20 is provided with three flattened surface regions 38 in total, equi-angularly spaced around the rider 20 so that each is co-operable with a respective one of the three tappets.
  • the rider 20 may therefore be considered to be of generally prismatic-type form.
  • the lower surface 37 of the tappet base 32 defines a surface edge 37a and the flattened surface 38 of the rider 20 defines a surface edge 38a.
  • the surface edge 37a of the tappet is of annular form and, effectively, defines a 'surface line'.
  • the surface 37 of the tappet base 32 and the facing flattened surface 38 of the cam rider 20 are co-operably shaped to provide an increased volume between them for lubricating fluid.
  • the lower surface of the tappet base 32 is provided with a recess to define a substantially concave surface 37, rather than being flat as is known in conventional tappet drive arrangements.
  • This relatively large fluid volume 44 is variable throughout the pumping cycle and provides a prolonged transient fluid pressure condition which serves to reduce friction between the surfaces 37, 38 as they translate or slide relative to one another, in use. The reason for this is described in further detail below. It should be noted that the extent to which the surface 37 of the tappet base 32 is concave is exaggerated greatly in Figure 2.
  • the pump assembly is provided with an appropriate inlet metering valve (not shown) with appropriate inlet and outlet valves (also not shown) being provided for each of the three pump chambers.
  • Pressurisation of fuel within the pump chamber 28 occurs during the pumping stroke of the plunger 24, during a period for which both the inlet and outlet valves are closed.
  • pressurised fuel is supplied through a delivery passage to the common rail.
  • the pressure of fuel supplied through the outlet valve is in the range of between 1500 and 2000 bar.
  • fuel pressure downstream of the pump chamber 28 is higher than that within the pump chamber 28 and the outlet valve is urged closed.
  • fuel at relatively low pressure is supplied to the pump chamber 28 to fill the chamber 28 ready for commencement of the following pumping stroke.
  • the surface 37 of the rider 20 moves laterally, back and forth, relative to the surface 37 of the tappet 30.
  • the relative velocity between the sliding surfaces 37, 38 varies through the pumping cycle, as shown in Figure 3 (it should be appreciated particularly that the vertical axis in Figure 3 represents relative velocity and not tappet displacement).
  • the volume 44 defined between them fills with, and dispels, lubricating fluid, in a cyclic manner, as described below with reference to Figures 4 and 5.
  • Figure 5(a) shows the tappet 30 and the plunger 24 at the start of the pumping stroke, at or just after BDC (a first stage of the pumping stroke), when the relative velocity between the sliding surfaces 37, 38 is, approximately, at its maximum value.
  • this point in the pumping cycle is identified at 50 and at this point fuel pressure in the pump chamber 28 is relatively low so that only a relatively low return load is exerted on the plunger 24 and the tappet 30 due to fuel pressure in the chamber 28.
  • the volume 44 of lubricating fluid between the surfaces 37, 38 is large at this stage due to the concavity of the tappet base 32, which volume 44 includes a small clearance defined between the surfaces 37, 38 in the region of the tappet edge 37a at the surface line. It is this large volume 44 of fluid between the surfaces 37, 38 which supports the hydraulic return loading of the tappet 30 due to fuel pressure in the pump chamber 28.
  • Figure 5(b) illustrates the tappet 30 and the plunger 24 at a point further through the pumping stroke, a part of the way between BDC and TDC, at which the relative velocity between the flattened rider surface 38 and the tappet surface 37 has decreased, progressively, to a minimum (a second stage of the pumping stroke).
  • the return load on the plunger 24 and tappet 30 is increasing at this stage, as fuel pressure in the pump chamber 28 is increasing.
  • the tappet base 32 has a degree of compliance so that, as the return load increases the base 32 is caused to be depressed slightly, thereby reducing the volume 44 between the surfaces 37, 38.
  • lubricating fluid is dispelled from the volume 44 at a relatively low rate, as determined by the size of the gap or clearance between the tappet edge 37a at the surface line and the flattened surface 38.
  • the dispelling of fluid from the volume 44 provides a squeeze film effect, which serves to reduce friction between the surfaces 37, 38.
  • transient fluid pressure between the surfaces 37, 38 is prolonged such that, at the point at which the return load on the plunger 24 and tappet 30 is at a maximum and friction between the surfaces 37, 38 is most significant, transient fluid pressure between the surfaces 37, 38 is sufficient to support return loading of the tappet 30.
  • This critical point in the pumping cycle occurs just prior to the outlet valve opening to deliver pressurised fuel within the pump chamber 38 to the rail, as it is at this point that fuel pressure in the chamber 28 is at a maximum.
  • the flow area through which fuel is dispelled from the volume 44 is small so as to sustain transient fluid pressure within the volume 44 for a significant period of time, and particularly during that part of the pumping stroke when loading of the tappet is at a maximum (part way between BDC and TDC).
  • This is achieved by shaping the tappet base 32 and the cam rider 20 to provide a restricted flow means between the tappet surface edge 37a and the flattened surface 38 of the rider 20. Any increased areas available for fluid flow from the volume 44 will serve to reduce the time for which transient fluid pressure supports return loading of the tappet 30, which is undesirable.
  • it is therefore important that the surface 37 of the tappet is made accurately concave to sustain the restricted fluid flow between the surfaces 37, 38 from the volume 44 at all stages of the pumping stroke.
  • the tappet and the rider surfaces 37, 38 remain aligned, and transient fluid pressure within the volume supports the return loading of the tappet for a prolonged period due to the relatively large volume 44 of fluid between the surfaces 37, 38 at the tappet edge 37a being dispelled at a very low rate.
  • Figure 6 shows an alternative embodiment to that shown in Figures 2 and 5, in which the surface 137 of the tappet base 32 is not made concave but instead is provided with a recess, of generally U-shaped cross section, to define an annular outer wall 48.
  • a lower annular surface 137a of the outer wall 48 is substantially flat and defines, together with the surface 38 of the cam rider 20, a restricted flow means for permitting fluid within the volume 44 to be dispelled at a relatively low rate as the tappet 30 performs the pumping stroke. It is one advantage of this embodiment that the contact area between the two surfaces 137a, 38 is increased during the final stages of the pumping stroke, and this has the effect of reducing surface contact stress.
  • the tappet base 32 cannot distort as much as for the first embodiment due to the shaping of the recessed surface 137, so that the volume 44 between the surfaces 137, 38 does not collapse totally at the third stage of the pumping stroke.
  • the surface 37 of the tappet base 32 and the surface 138 of the cam rider 20 are both shaped to be concave so as to further increase the volume 44 available for lubricating fluid.
  • both surfaces 37, 138 are shaped with a high degree of accuracy so as to ensure a sufficiently restricted flow area for fluid is maintained at all times through the pumping stroke in the region of their surface contact.
  • Figure 8 shows a further alternative embodiment in which the tappet 30 is shaped in a similar manner to that shown in Figures 2 to 5, with the tappet base 32 being provided with a substantially recessed lower surface 237, but with its edge surface 237a being radiussed or 'rolled'.
  • Radiussing of the edge surface 237a provides a first advantage that, during the return stroke of the plunger and tappet when the volume 44 is being filled with lubricating fluid through the clearance gap between the edges 237a, 38a, the radiussed outermost edge encourages fluid to be drawn between the surfaces 237a, 38 into the volume 44.
  • a second advantage is obtained in that the contact area between the two surfaces 237a, 38 is increased during the final stages of the pumping stroke, thereby reducing surface contact stress.
  • the tappet and rider arrangements having the general constructions shown in Figures 6 and 8 may also be configured such that the surface edge of the tappet, which co-operates with the surface of the rider 20 to define the restricted flow means, is radiussed or rolled.
  • the recessed surface 37, 137, 237 of the tappet 30 may be further desirable to provide the recessed surface 37, 137, 237 of the tappet 30 with a plurality of small indentations or pockets to further enhance the available volume 44 for lubricating fluid. This may be achieved, for example, by forming laser pockets over the recessed tappet surface 37, 137, 237, or by rough grinding the recessed surface followed by super finishing.
  • each of the three flattened surfaces of the rider 20, and the respective co-operable surfaces of the three tappets may be shaped in the same manner as described for any of the aforementioned embodiments, or in an otherwise co-operably shaped manner to provide the functional benefit of the drive arrangement set out in the accompanying claims.
  • drive arrangement of the present invention may or may not be manufactured to include the cam 18 and/or the plunger 24. It will also be appreciated that drive arrangement of the present invention may be employed in other types of pump assembly, not necessarily radial pump assemblies and not necessarily pump assemblies of the type having three plungers.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (11)

  1. Dispositif d'entraînement pour plongeur de pompe (24) d'un ensemble de pompe, le dispositif d'entraînement comprenant un élément d'entraînement (30) qui peut coopérer avec le plongeur de pompe (24) et avec un poussoir de came (20) de manière à imprimer un entraînement axial au plongeur (24) pour exécuter une course de pompage de plongeur tout en permettant un mouvement de coulissement latéral du poussoir (20) par rapport à l'élément d'entraînement (30),
    caractérisé en ce que l'élément d'entraînement (30) et le poussoir de came (20) sont formés de manière coopérante afin de définir (i) un volume (44) pour du fluide de graissage qui est variable à travers le cycle de pompage et (ii) des moyens d'écoulement contrarié à travers lesquels le fluide à l'intérieur dudit volume (44), est refoulé à une vitesse relativement basse tandis que le plongeur (24) est entraîné à travers toute la course de pompage de manière à prolonger la pression du fluide transitoire à l'intérieur du volume (44) à travers cette période de la course de pompage pour laquelle la charge de retour de l'élément d'entraînement (30) est à un maximum.
  2. Dispositif d'entraînement selon la revendication 1, dans lequel au moins l'un parmi l'élément d'entraînement (30) et le poussoir (20) est façonné de manière à définir une surface renfoncée (37, 38 ; 137, 38 ; 37, 138 ; 237, 38) qui définit, conjointement avec une surface de l'autre parmi l'élément d'entraînement (30) et le poussoir (20), ledit volume variable pour fluide (44).
  3. Dispositif d'entraînement selon la revendication 2, dans lequel la surface renfoncée (37) de l'élément d'entraînement (30) est sensiblement concave.
  4. Dispositif d'entraînement selon la revendication 2 ou 3, dans lequel le poussoir de came (20) comprend une surface sensiblement aplatie (38) qui définit, conjointement avec la surface concave (37) de l'élément d'entraînement (30), le volume variable pour fluide (44).
  5. Dispositif d'entraînement selon la revendication 2 ou 3, dans lequel le poussoir de came (20) comprend une surface sensiblement concave (138) qui définit, conjointement avec la surface (37) de l'élément d'entraînement (30), le volume variable pour fluide (44).
  6. Dispositif d'entraînement selon l'une quelconque des revendications 3 à 5, dans lequel les moyens d'écoulement contrarié sont définis par un bord de surface (37a) de la surface renfoncée (37) de l'élément d'entraînement (30) et la surface (38) du poussoir (20).
  7. Dispositif d'entraînement selon la revendication 2, dans lequel l'élément d'entraînement (30) est muni d'un renfoncement sensiblement en forme de U afin de définir la surface renfoncée (137).
  8. Dispositif d'entraînement selon la revendication 7, dans lequel l'élément d'entraînement (30) est façonné de manière à définir une paroi latérale d'élément d'entraînement (48) de forme annulaire définissant une surface annulaire (137a) qui peut coopérer avec la surface du poussoir (20) pour définir les moyens d'écoulement contrarié.
  9. Dispositif d'entraînement selon l'une quelconque des revendications 6 à 8, dans lequel les moyens d'écoulement contrarié sont définis par une surface arrondie (237a) de l'élément d'entraînement (30) et la surface (38) du poussoir (20).
  10. Dispositif d'entraînement selon l'une quelconque des revendications 1 à 9, dans lequel l'élément d'entraînement est un poussoir de soupape (30).
  11. Ensemble de pompe comprenant un plongeur et un dispositif d'entraînement pour le plongeur selon l'une quelconque des revendications 1 à 10.
EP03253852A 2003-06-18 2003-06-18 Système d'entraînement pour une Pompe Expired - Lifetime EP1489301B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE60309145T DE60309145T2 (de) 2003-06-18 2003-06-18 Antriebsanordnung für eine Pumpe
AT03253852T ATE343060T1 (de) 2003-06-18 2003-06-18 Antriebsanordnung für eine pumpe
EP03253852A EP1489301B1 (fr) 2003-06-18 2003-06-18 Système d'entraînement pour une Pompe

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP03253852A EP1489301B1 (fr) 2003-06-18 2003-06-18 Système d'entraînement pour une Pompe

Publications (2)

Publication Number Publication Date
EP1489301A1 EP1489301A1 (fr) 2004-12-22
EP1489301B1 true EP1489301B1 (fr) 2006-10-18

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP03253852A Expired - Lifetime EP1489301B1 (fr) 2003-06-18 2003-06-18 Système d'entraînement pour une Pompe

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EP (1) EP1489301B1 (fr)
AT (1) ATE343060T1 (fr)
DE (1) DE60309145T2 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB0602742D0 (en) 2005-06-06 2006-03-22 Delphi Tech Inc Machining method
EP1780415B1 (fr) 2005-10-25 2015-08-05 Delphi International Operations Luxembourg S.à r.l. Composant pour des applications de fluides sous hautes pressions et procédé pour sa réalisation
JP2023013759A (ja) 2021-07-16 2023-01-26 株式会社Soken サプライポンプ
CN115807748A (zh) * 2022-12-07 2023-03-17 北京天玛智控科技股份有限公司 柱塞滑靴组件和多边形轮盘驱动的径向柱塞泵

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2909248C2 (de) * 1979-03-09 1984-03-15 J.M. Voith Gmbh, 7920 Heidenheim Arbeitskolben für eine hydrostatische Kolbenmaschine
DE19705205A1 (de) * 1997-02-12 1998-08-13 Bosch Gmbh Robert Kolbenpumpe
DE19814506A1 (de) * 1998-04-01 1999-10-14 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckversorgung
DE19836901C2 (de) * 1998-08-14 2002-08-29 Bosch Gmbh Robert Radialkolbenpumpe
JP2002004978A (ja) * 2000-06-19 2002-01-09 Nachi Fujikoshi Corp 高圧プランジャポンプの強制潤滑装置

Also Published As

Publication number Publication date
EP1489301A1 (fr) 2004-12-22
DE60309145T2 (de) 2007-08-16
ATE343060T1 (de) 2006-11-15
DE60309145D1 (de) 2006-11-30

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