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WO2000019095A1 - Pompe a pistons radiaux - Google Patents

Pompe a pistons radiaux Download PDF

Info

Publication number
WO2000019095A1
WO2000019095A1 PCT/DE1999/002838 DE9902838W WO0019095A1 WO 2000019095 A1 WO2000019095 A1 WO 2000019095A1 DE 9902838 W DE9902838 W DE 9902838W WO 0019095 A1 WO0019095 A1 WO 0019095A1
Authority
WO
WIPO (PCT)
Prior art keywords
tappet
piston pump
holes
radial piston
lubrication
Prior art date
Application number
PCT/DE1999/002838
Other languages
German (de)
English (en)
Inventor
Rainer Haeberer
Hans-Jürgen Simon
Thomas Schwarz
Original Assignee
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 Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2000019095A1 publication Critical patent/WO2000019095A1/fr

Links

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
    • F04B1/0439—Supporting or guiding means for the pistons
    • 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
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders

Definitions

  • the invention relates to a radial piston pump for generating high fuel pressure
  • Fuel injection systems of internal combustion engines in particular in the case of a common rail injection system with a drive shaft mounted in a pump housing, which has an eccentric shaft section on which a polygon ring is supported, on which a plurality of pistons, which are arranged radially with respect to the drive shaft, are supported, which can be moved back and forth in the radial direction in the respective element bore by rotating the drive shaft.
  • the base of the piston is in contact with the polygon ring mounted on the eccentric shaft section of the drive shaft. Due to the eccentricity of the eccentric shaft portion of the drive shaft, the pistons are reciprocated one after the other. During operation, the polygon ring applies forces to the pistons. The lines of action of these forces extend both lengthways and across the pistons.
  • the object of the present invention is to provide a radial piston pump with a long service life, in which the bearing surface of the piston foot on the polygon ring is optimized, in particular when the cylinder spaces are partially filled.
  • the radial piston pump according to the invention is designed to withstand a pump pressure of up to 2,000 bar.
  • Fuel injection systems of internal combustion engines in particular in a common rail injection system, with a drive shaft mounted in a pump housing, which has an eccentric shaft section on which a polygon ring is supported, on which a plurality of pistons, which are arranged radially with respect to the drive shaft, are supported , by
  • Rotation of the drive shaft in the respective element bore can be moved back and forth in the radial direction, in that a cup tappet is arranged between the piston and the drive shaft, the bottom of which has a chamfer on the side facing the drive shaft.
  • the tappet absorbs the lateral forces acting across the pistons. This has the advantage that only longitudinal forces are applied to the pistons.
  • the pistons are decoupled from the polygon ring. This significantly reduces the load on the pistons from the drive shaft.
  • the chamfer optimizes the contact surface of the tappet on the polygon ring. Suitable geometrical dimensions ensure that the contact surface of the tappet on the polygon ring does not migrate beyond the edges of flats on the surface during operation Polygon ring are formed.
  • a special embodiment of the invention is characterized in that several through holes are left in the area of the chamfer.
  • the through holes allow lubricant to pass through. This ensures that the lubricating film does not tear off at the contact point between the bottom of the tappet and the running surface of the polygon ring.
  • the attachment of the through holes in the area of the chamfer provides the
  • the advantage is that the contact surface of the tappet on the polygon ring is not interrupted. This promotes the formation of a lubricating film.
  • the through holes also ensure pressure equalization when the bucket tappet moves back and forth in the element bore.
  • a radial piston pump for high-pressure fuel generation in fuel injection systems of internal combustion engines in particular in a common rail injection system, with a drive shaft mounted in a pump housing, which has an eccentric shaft section on which a polygon ring is mounted, on which several are preferably radial with respect to the drive shaft
  • Support pistons arranged in a respective element bore which can be moved back and forth in the respective element bore in the radial direction by rotating the drive shaft, in that a cup tappet is arranged between the piston and the polygon ring, several in the bottom of which
  • Through holes are recessed.
  • the through holes serve for the passage of lubricant. This favors the formation of a lubricating film on the contact surface of the tappet on the polygon ring.
  • the installation of the through holes only in the bottom of the
  • Cup tappet provides the advantage that the guide surface of the bucket tappet remains intact in the element bore.
  • a special embodiment of the invention is characterized in that the through holes are designed as elongated holes.
  • the elongated holes provide better access for an assembly tool. This simplifies the assembly of the bucket tappet when assembling the radial piston pump.
  • a further special embodiment of the invention is characterized in that the bucket tappet has a cylindrical body, in the outer lateral surface of which a lubrication groove is made, and that in the area of the lubrication grooves, a plurality of lubrication holes are made.
  • a further special embodiment of the invention is characterized in that a lubrication hole is provided in the center transverse to the bottom of the cup tappet, which is connected to a plurality of lubrication channels which run radially outward from the lubrication hole and open in the area of the through holes. This improves the lubrication between the bottom of the tappet and the tread of the polygon ring. That has the
  • Another special embodiment of the invention is characterized in that the bottom of the tappet has a counterbore on the side facing the piston.
  • Another special embodiment of the invention is characterized in that the bottom of the bucket tappet is formed on the side facing the drive shaft from a material that has a low coefficient of friction. This can be done alternatively through the insert
  • This embodiment has the advantage that the friction between the bottom of the tappet and the tread of the polygon ring is minimized. As a result, the lateral forces to be supported in the cylinder space are reduced.
  • FIG. 1 shows the view of a section through a Radial piston pump according to an embodiment of the present invention transverse to the drive shaft;
  • FIG. 2 shows an enlarged view of the detail X from FIG. 1;
  • FIG. 3 shows an enlarged view of detail Y from FIG. 1;
  • Figure 4 shows the tappet from Figure 1 in the bottom view.
  • FIG. 5 shows the view of a section along the line A-A in Fig. 6;
  • FIG. 6 the cup tappet from FIG. 1 in a top view
  • FIG. 7 shows the view C of the tappet from FIG. 6
  • Figure 8 is a sectional view taken along line B-B in Figure 6;
  • Figure 9 shows a tappet according to another
  • Figure 10 is a sectional view taken along line A-A in Figure 11;
  • FIG. 11 the cup tappet from FIG. 9 in a top view
  • Figure 12 shows a tappet according to another
  • FIG. 13 shows the view of a section along the line AA in Fig. 15;
  • FIG. 14 is an enlarged view of detail Y from FIG. 13;
  • FIG. 15 the cup tappet from FIG. 12 in a top view
  • Figure 16 shows a tappet according to another
  • Figure 17 is a sectional view taken along line A-A in Figure 18;
  • FIG. 18 the cup tappet from FIG. 16 in a top view
  • Figure 19 is a tappet according to another
  • Figure 20 is a sectional view taken along line A-A in Figure 21;
  • FIG. 21 the cup tappet from FIG. 19 in a top view
  • FIG. 22 shows an enlarged view of the detail X from FIG. 20;
  • FIG. 23 is an enlarged view of detail Y from FIG. 20;
  • Figure 24 shows a tappet according to another
  • FIG. 25 shows the view of a section along the line AA in Fig. 26;
  • FIG. 26 the cup tappet from FIG. 24 in a top view
  • Figure 27 is an enlarged view of detail X from
  • Figure 28 is an enlarged view of detail Y from
  • Figure 29 shows a tappet according to another
  • Figure 30 is a sectional view taken along line A-A in Figure 31;
  • FIG. 31 the cup tappet from FIG. 29 in a top view
  • Figure 32 shows a tappet according to another
  • Figure 33 is a sectional view taken along line A-A in Figure 34;
  • FIG. 34 the cup tappet from FIG. 32 in a top view
  • Figure 35 is an enlarged view of the section shown in Fig. 20 with a piston.
  • FIG. 1 shows a radial piston pump for supplying high-pressure fuel in fuel injection systems of internal combustion engines
  • the radial piston pump shown in Fig. 1 is equipped with an integrated demand control.
  • the fuel supply and dimensioning takes place via a metering unit, not shown.
  • the radial piston pump according to the invention is used in particular in common rail injection systems for supplying fuel to diesel engines.
  • Common rail means something like common line or common rail.
  • the injection nozzles in common-rail injection systems are fed from a common line.
  • the radial piston pump shown in FIG. 1 comprises a drive shaft 2, which is mounted in a pump housing 1 and has an eccentrically designed shaft section 3.
  • a polygon ring 4 is mounted on the eccentric shaft section 3, with respect to which the shaft section 3 can be rotated.
  • the polygon ring 4 comprises three flats 5, 6 and 7, each offset by 120 ° to each other, against which a piston 8, 9 and 10 is supported.
  • the pistons 8, 9 and 10 are each received in an element bore 11, 12 and 13 so that they can move back and forth in the radial direction relative to the drive shaft 2.
  • the foot 14, 15 and 16 can either be formed in one piece with the piston 8, 9 and 10 or can be removably attached to it. Against the plate 14, 15 and
  • the 16 is a spring 17, 18 and 19 biased.
  • the spring 17, 18 and 19 presses the piston 8, 9 and 10 against the bottom 20, 21 and 22 of a tappet 23, 24 and 25.
  • From the bottom 20, 21 and 22 of the tappet 23, 24 and 25 a cylindrical one extends Guide body 26, 27 and 28.
  • the Guide body 26, 27 and 28 is displaceable in a guide bore 29, 30 and 31 in the housing 1.
  • the radial piston pump shown in Fig. 1 is used to apply high pressure to fuel that is supplied from a prefeed pump from a tank. The high pressure fuel is then fed into the above. joint management promoted.
  • the pistons 8, 9 and 10 are moved away from the axis of the drive shaft 2 as a result of the eccentric movement of the polygon ring 4.
  • the pistons 8, 9 and 10 move radially towards the axis of the drive shaft 2 in order to draw in fuel.
  • a 'chamfer 36 is formed at the bottom 22 of the cup tappet 25 .
  • the chamfer 36 is dimensioned such that the circumferential edge 37 of the cup tappet 25 does not come into contact with the flat 7 of the polygon ring 4 during operation. This results in a particularly low-wear interaction between the bottom 22 of the tappet 25 and the flattened portion 7 of the polygon ring 4.
  • FIGS. 4 to 8 one of the tappets 23 to 25 shown in FIGS. 1 to 3 is shown alone in different views.
  • the bottom view shown in FIG. 4 it can be seen that the bottom 20 of the cup tappet is equipped with a circular contact surface 40. Concentric to the bearing surface 40 is in the bottom 20 of the tappet, as can be seen in FIG. 5 is a chamfer 45 is formed. In the area of the chamfer 45, four through holes 41, 42, 43 and 44 are recessed which extend into the guide body 26. The geometric shape of the through holes 41 to 44 can be seen from the views shown in FIGS. 4 to 8. It can be seen from the bottom view shown in FIG. 4 and the top view shown in FIG.
  • the parts of the through holes 41 to 44 arranged in the base 20 have the shape of a rectangle with rounded edges. It can be seen from the views shown in FIGS. 7 and 8 that the parts of the through holes 41 to 44 arranged in the guide body 26 each have the shape of a rectangle which ends in a semicircular arc.
  • FIGS. 12 to 14 The embodiment of a tappet according to the invention shown in FIGS. 12 to 14 largely corresponds to the embodiment shown in FIGS. 9 to 11.
  • four lubrication bores 47 offset from one another by 90 ° are attached in the guide body 26.
  • the lubrication bores 47 run in the radial direction in the cylindrical guide body 26, as can be seen in FIG. 13.
  • the cross 48 in FIG. 15 indicates that the lubrication bores 47 can each be arranged offset by 45 ° to the through holes 41 to 44.
  • the lubrication bores 47 open into a lubrication groove 46, which in the outer lateral surface of the guide body 26 is recessed.
  • the through holes 41 to 44 are formed as elongated holes, in contrast to the embodiments shown in FIGS. 9 to 14.
  • FIGS. 19 to 23 The embodiment of a tappet according to the invention shown in FIGS. 19 to 23 largely corresponds to the embodiment shown in FIGS. 12 to 14. In contrast to this, however, as can best be seen from the enlarged illustration of the detail Y from FIG. 20 in FIG. 22, a lubrication bore 50 is provided in the center of the base 20.
  • Bucket tappet 23 opens the lubrication hole 50 in a depression 53.
  • two lubrication channels 51 and 52 extend from the lubrication hole 50 in the radial direction.
  • dashed lines indicate that the lubrication channels 51 and 52 open into the through holes 41 and 43.
  • each through hole 41 to 44 can also be connected to the lubrication bore 50 via a lubrication channel.
  • a further embodiment of a tappet according to the invention is shown in different views.
  • This embodiment represents a combination of elongated holes 41 to 44, a lubricating groove 46 with lubricating bores 47 and a lubricating bore 50 with lubricating channels 51 and 52.
  • the lubricating channels 51 and 52 do not open into the elongated holes 41 to 44, but are arranged offset by 45 ° to the elongated holes. This means that the lubrication channels 51 and 52 are arranged parallel to the lubrication bores 47. 29 to 31 and 32 to 34 two further embodiments of a tappet according to the invention are shown.
  • the two embodiments have in common that the through holes 41 to 44 are arranged only in the bottom 20 of the tappet 23.
  • an insert 54 made of a different material is arranged on the outside in the base 20.
  • This other material can for example consist of a plain bearing material and has a lower coefficient of friction than the material from which the tappet 23 is made. This minimizes the friction between the tappet 23 and the polygon ring 4.
  • Fig. 35 the cup tappet 23 shown in Figs. 19 to 23 is shown together with a piston 8.
  • the seat 53 of the piston 8 is optimized by the depression 53.
  • the edge of the lubrication bore 50 is relieved.
  • the end of the piston 8 in contact with the countersink 53 is slightly spherical. This results in an optimal force and pressure curve during operation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

Pompe à pistons radiaux destinée à produire une haute pression de carburant dans des systèmes d'injection de carburant de moteurs à combustion interne. Ladite pompe comporte un arbre menant (2), placé dans un carter (1) de pompe, qui présente une partie (3) excentrique sur laquelle est montée une bague polygonale (4) sur laquelle s'appuient de préférence plusieurs pistons placés chacun radialement par rapport à l'arbre menant (2) dans un alésage (11 à 13), lesdits pistons effectuant un mouvement de va-et-vient dans le sens radial dans leur alésage (11 à 13) par rotation de l'arbre menant (2). L'usure de la pompe à pistons radiaux est réduite du fait qu'entre le piston (8 à 10) et la bague polygonale (4) est placé un poussoir dont le fond (20 à 22) comporte un chanfrein sur la face orientée vers l'arbre menant (2). Dans une variante de la présente invention, plusieurs trous traversants sont ménagés dans le fond (20 à 22) du poussoir (23 à 25).
PCT/DE1999/002838 1998-09-28 1999-09-08 Pompe a pistons radiaux WO2000019095A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19844326.9 1998-09-28
DE1998144326 DE19844326B4 (de) 1998-09-28 1998-09-28 Radialkolbenpumpe

Publications (1)

Publication Number Publication Date
WO2000019095A1 true WO2000019095A1 (fr) 2000-04-06

Family

ID=7882440

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1999/002838 WO2000019095A1 (fr) 1998-09-28 1999-09-08 Pompe a pistons radiaux

Country Status (2)

Country Link
DE (1) DE19844326B4 (fr)
WO (1) WO2000019095A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009097517A (ja) * 2007-10-18 2009-05-07 Delphi Technologies Inc ポンプアッセンブリ及びこのポンプアッセンブリ用のタペット

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10345089A1 (de) * 2003-09-26 2005-04-21 Bosch Gmbh Robert Stößel für eine Hochdruckpumpe und Hochdruckpumpe mit wenigstens einem Stößel
DE102004023541A1 (de) 2004-05-13 2005-12-01 Robert Bosch Gmbh Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102004053270A1 (de) * 2004-11-04 2006-05-11 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102004056940A1 (de) * 2004-11-25 2006-06-01 Schaeffler Kg Stößel für eine Hochdruckeinspritzpumpe
DE102007018038A1 (de) 2007-04-13 2008-10-16 Robert Bosch Gmbh Kraftstoffpumpe für ein Kraftstoffsystem einer Brennkraftmaschine
DE102008001713A1 (de) 2008-05-13 2009-11-19 Robert Bosch Gmbh Radialkolbenpumpe
IT1395139B1 (it) * 2009-08-06 2012-09-05 Bosch Gmbh Robert Pompa di alta pressione per alimentare combustibile ad un motore a combustione interna
IT1401971B1 (it) * 2010-09-27 2013-08-28 Bosch Gmbh Robert Pompa di alta pressione per alimentare combustibile ad un motore a combustione interna

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0304743A1 (fr) * 1987-08-25 1989-03-01 WEBER S.r.l. Pompe à pistons radiaux
EP0809023A2 (fr) * 1996-05-23 1997-11-26 Lucas Industries Public Limited Company Pompe à pistons radiaux
DE19727249A1 (de) * 1996-07-01 1998-01-08 Rexroth Mannesmann Gmbh Vorrichtung zur Stabilisierung des Exzenterrings einer Radialkolbenpumpe
DE19753593A1 (de) * 1997-12-03 1999-06-17 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckversorgung

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3721698A1 (de) * 1987-07-01 1989-01-19 Hauhinco Maschf Radialkolbenpumpe fuer die foerderung von wasser

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0304743A1 (fr) * 1987-08-25 1989-03-01 WEBER S.r.l. Pompe à pistons radiaux
EP0809023A2 (fr) * 1996-05-23 1997-11-26 Lucas Industries Public Limited Company Pompe à pistons radiaux
DE19727249A1 (de) * 1996-07-01 1998-01-08 Rexroth Mannesmann Gmbh Vorrichtung zur Stabilisierung des Exzenterrings einer Radialkolbenpumpe
DE19753593A1 (de) * 1997-12-03 1999-06-17 Bosch Gmbh Robert Radialkolbenpumpe zur Kraftstoffhochdruckversorgung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009097517A (ja) * 2007-10-18 2009-05-07 Delphi Technologies Inc ポンプアッセンブリ及びこのポンプアッセンブリ用のタペット

Also Published As

Publication number Publication date
DE19844326B4 (de) 2006-01-05
DE19844326A1 (de) 2000-04-06

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