EP0862693A1 - Pompe a piston - Google Patents

Pompe a piston

Info

Publication number
EP0862693A1
EP0862693A1 EP97925877A EP97925877A EP0862693A1 EP 0862693 A1 EP0862693 A1 EP 0862693A1 EP 97925877 A EP97925877 A EP 97925877A EP 97925877 A EP97925877 A EP 97925877A EP 0862693 A1 EP0862693 A1 EP 0862693A1
Authority
EP
European Patent Office
Prior art keywords
piston
sliding
pump according
piston pump
cam ring
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
EP97925877A
Other languages
German (de)
English (en)
Other versions
EP0862693B1 (fr
Inventor
Hans-Peter Stiefel
Karl Gmelin
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 GmbH
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 EP0862693A1 publication Critical patent/EP0862693A1/fr
Application granted granted Critical
Publication of EP0862693B1 publication Critical patent/EP0862693B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • 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
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/04—PTFE [PolyTetraFluorEthylene]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/12—Coating

Definitions

  • the invention relates to a piston pump, in particular a high-pressure pump for a fuel injection device of an internal combustion engine, according to the preamble of claim 1.
  • the power transmission from the eccentric pin to the piston takes place by means of flexible transmission elements which are fastened to the piston and the cup-shaped part, which is not rotating, mounted on the drive shaft, so that between the piston and its actuating element, i.e. the cup-shaped part, or the transmission elements no sliding friction occurs.
  • a radial piston pump with external piston support in which a cylinder star is rotated by a drive shaft via a clutch during operation of the pump.
  • the cylinder star has a large number of cylinders in which pistons are arranged to be radially displaceable.
  • the cylindrical star with the pistons is circumferentially surrounded by a substantially non-rotatable cam ring, on the inner circumferential surface serving as a sliding bearing surface, the pistons are supported with their radially outer ends via sliding shoes.
  • each slide shoe has a recess in the middle of its slide surface, which is connected to the respective cylinder space.
  • grooves extending transversely to the direction of movement are also provided in the sliding surfaces of the sliding shoes.
  • the piston pump with the characterizing features of claim 1 has the advantage that high transverse forces on the pistons, which would have to be absorbed by the piston guide, are avoided.
  • one-sided transverse forces, such as occur in conventional radial piston pumps, are prevented without the need for expensive actuating elements between the cam ring and the piston.
  • a particular advantage of the invention is that the medium to be conveyed by the pump reaches all areas between the slide bearing surface on the cam ring and the slide shoe, although the cam ring only performs an oscillating slide movement with respect to the slide shoe, the displacement length of which is less than the length the sliding surface on the sliding block in the direction of displacement.
  • cam ring made of plastic, in particular of polyimide or PEEK, is particularly advantageous since this creates particularly low-friction bearing surfaces, so that additional bearing elements between the cam ring and crank element as well as measures to improve the friction on the sliding surface arranged on the piston can be dispensed with.
  • coatings in particular carbon coatings, on the sliding surface arranged on the piston and on the circumferential surface running in the piston guide of the piston improves the corresponding surface hardness and wear resistance, so that so-called seizures between the sliding surfaces can be prevented.
  • FIG. 1 shows a longitudinal section through a piston pump according to the invention
  • FIG. 2 is a partially sectioned view of the piston pump according to FIG. 1 in the plane of the piston,
  • FIG. 3a shows a plan view of a cam ring for a piston pump according to the invention
  • 3b is a plan view of a slide bearing surface of the cam ring in the direction of arrows b in FIG. 3a,
  • FIG. 3c is an enlarged view of area C in FIGS. 3a and
  • Fig. 4 is a partially sectioned schematic representation of another piston pump according to the invention.
  • a housing 10 of a preferably selected piston pump designed according to the invention has a bearing section 11 and a pump section 12 which are connected to one another by means of screw bolts 13, only one of which is shown.
  • a drive shaft 14 is supported in the bearing section 11 by means of a roller bearing 15.
  • the rolling bearing 15 is formed by a bearing outer ring 16 and the drive shaft 14, into which ball tracks 17 for bearing balls 18 serving as rolling elements are ground.
  • end seals 19 are provided between the bearing outer ring 16 and the drive shaft 14, so that the inner region of the roller bearing 15 is sealed.
  • a drive disk 21 which carries a ring gear 22, is fitted in a rotationally fixed manner on a shaft journal 20 protruding from the housing 10.
  • a low-pressure chamber 23 provided in the housing 10 is sealed off from the rolling bearing 15 by means of an axial shaft seal 24.
  • a leakage nozzle 25 is inserted tightly into a corresponding opening 26 in the bearing section 11 of the housing 10.
  • an eccentric pin 27 is arranged as a crank element, on which a cam ring 28 is mounted by means of a bearing sleeve 29.
  • the bearing sleeve 29 has at its end facing away from the free end of the eccentric pin 27 a radial flange 30 with which it rests on a shoulder 31 of the drive shaft 14.
  • Support disc 32 is attached to the end face of the eccentric pin 27 by means of a retaining bolt 33 or the like.
  • the bearing sleeve 29 which is made of metal, preferably made of steel, has a bearing surface made of plastic, preferably of a thermoplastic, in particular of a thermoplastic serving as a solid lubricant.
  • plastic preferably of a thermoplastic, in particular of a thermoplastic serving as a solid lubricant.
  • the plastic can be PTFE (polytetrafluoroethylene), PTFE with lead as filler, acetal copolymer, or a combination of PEEK (polyether ether ketone) and PTFE and a suitable filler.
  • the support disk 32 is preferably made of the same material as the bearing sleeve 29.
  • the lifting ring 28 has flat slide bearing surfaces 34, on each of which a slide shoe 36 which is fastened to a piston 35 is supported.
  • Each of the sliding shoes 36 comprises a body 38 fastened to the piston 35 by means of a clamp ring 37 and a sliding plate 39 fastened thereon, which serves as a sliding element and has a sliding surface 40 resting on the sliding bearing surface 34.
  • lubrication grooves 41 are provided in the slide bearing surfaces 34 of the cam ring 28, which are parallel to the direction of displacement of the displacement movement extend to each other.
  • the cross section of the lubrication grooves 41 is essentially V-shaped.
  • the opening angle ⁇ of the lubrication grooves 41 is approximately 90 °.
  • the tip of the V-shaped cross section of the lubrication grooves 41 is rounded.
  • the lubrication grooves 41 can also have a smaller, but preferably a larger, opening angle ⁇ .
  • the opening angle ⁇ can be up to approximately 120 °.
  • a lubricating wedge, the wedge angle of which is approximately 30 ° to 45 °, can thus form between the flanks 41 'and the sliding shoe 36, not shown in FIGS. 3a and 3c.
  • the lubrication grooves 41 can also have a different cross section. Semicircular or part-circular cross-sections with and without rounded edges are possible, as are sinusoidal cross-sections. In particular, it is expedient if the edges 41 ′′ of the lubrication grooves 41 are rounded such that the flanks 41 ′ of the lubrication grooves 41 pass over the edges 41 ′′ essentially tangentially into the slide bearing surface 34. In this way, an optimal lubricating wedge can be achieved.
  • the distance d (see FIG. 3b) between the lubrication grooves 41 is at most as large as the piston stroke of the piston 35.
  • the partial dimension T which consists of the distance d between the lubrication grooves 41 and the width b of the lubrication grooves 41, is smaller as or as large as the piston stroke.
  • the slide plates held therein are preferably made of plastic, in particular of PEEK or of polyimide.
  • a slide plate 39 can also be used be made of steel, which is provided with a metal-free or metal-containing carbon coating.
  • Such a coating brings about an improvement in the surface hardness and a reduction in sliding friction.
  • the wettability of the surface is improved by a carbon coating, so that a lubricating film from the medium to be conveyed can form more easily between the sliding surface 40 and the sliding bearing surface 34.
  • a one-piece sliding shoe 36 ' (FIG. 4) instead of the sliding shoe 36 described, which is made of plastic or steel.
  • the piston 35 guided in a piston guide 42 is supported by a spring 43, which is supported on the one hand via the clamp ring 37 on the slide shoe 36 and on the other hand on a holding part 44 into which the piston guide 42 is inserted, pressed against the slide bearing surface 34 of the cam ring 28.
  • a working chamber 45 is provided in the holding part 44 and in the piston guide 42, which is connected to the low-pressure chamber 23 via an inlet valve 46 connected to the piston 35, an axial inlet bore 47 provided in the piston 35, and inlet openings 48 arranged in the piston 35, when the piston 35 moves during a rotation of the drive shaft 14 in the direction of the drive shaft axis A.
  • the working space 45 is delimited by a valve 52.
  • the medium to be pumped is fed to the low-pressure region 23 via corresponding inlet connections 53.
  • the eccentric pin 27 rotates with an eccentricity e about the drive shaft axis A and thereby sets the cam ring 28 in a circular movement about the drive shaft axis A.
  • the cam ring 28 does not perform a rotational movement since it moves over the adjacent sliding shoes 36 is not held in rotation by the pistons 35.
  • the lubrication grooves 41 are arranged in the slide bearing surface 34 of the cam ring 28 at a distance d which is smaller than the piston stroke, that is to say at a distance which is smaller than the displacement path of the slide shoe 36 against the cam ring 38, it can be conveyed with each displacement movement Medium from one of the lubrication grooves 41 in the slide bearing surface 34 are taken from the slide surface 40 to the adjacent lubrication groove 41. Thus, the medium to be conveyed reaches all areas between the sliding bearing surface 34 and the sliding surface 40 and dry running of this sliding bearing is reliably prevented.
  • the lubrication grooves 41 can also be arranged at an oblique angle to the direction of the sliding movement.
  • the cam ring 28 Since the cam ring 28 carries out an oscillating displacement movement with its slide bearing surface 34 with respect to the piston 35 or the slide shoe 36, one-sided loads on the piston guide 42 are avoided. In addition, the good The sliding bearing of the sliding shoe 36 on the lifting ring 28 on the piston 35 acting transverse forces is significantly reduced. As a result, the wear of piston 35 and piston guide 42 can be significantly reduced, which leads to a considerable extension of the service life of the piston pump according to the invention. In order to further reduce the wear on the surfaces of the piston 35 and piston guide 42 sliding on one another and to reduce any pressure fields that may arise in this area, the piston 35 can be provided with circumferential grooves 54. In addition, it is also possible to coat the piston, which is preferably made of steel, with a metal-containing or metal-free carbon layer.
  • FIG. 4 Another embodiment of the piston pump according to the invention shown in FIG. 4 has a one-piece sliding shoe 36 'which interacts with a cam ring 28 mounted directly on the eccentric pin 27 of the drive shaft 14.
  • the cam ring 28 expediently consists of plastic, in particular of a high temperature-resistant thermoplastic, preferably of PEEK or of polyimide.
  • the slide shoe 36 'advantageously consists of steel, and its slide surface 40' can be coated with a carbon layer.
  • the carbon layer used to improve friction can be metal-free or metal-containing.
  • cam ring 28 made of PEEK or polyimide, corrosion problems that can occur with a metal cam ring are avoided. Since the preferred plastics are low-friction, a bearing sleeve between the eccentric pin 27 and the cam ring 28 can be dispensed with at the same time, which further simplifies the construction of the piston pump according to the invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)

Abstract

La présente invention concerne une pompe à piston, et plus particulièrement un pompe haute pression pour le système d'injection de carburant d'un moteur à combustion interne, comprenant au moins un piston (35) monté coulissant sur paliers à l'intérieur d'un guide de piston (42) prévu dans le carter (10) où est installé l'arbre de commande (14) doté d'un élément de de manivelle (27), ainsi qu'une bague de piston (28) montée rotative sur l'élément de manivelle (27), sur laquelle le piston (35) associé à l'arbre de commande (14) peut prendre appui. Pour éviter que d'importantes forces transversales ne s'exercent sur le piston (35), il est prévu que celui-ci (35) prenne appui sur la bague de piston (28) non rotative par la surface frottante prévue pour lui sur la surface des paliers à friction (34), qui présente, dans un axe transversal par rapport au mouvement relatif, des cannelures de lubrification (41) entre le piston (35) et la bague de piston (28).
EP97925877A 1996-08-30 1997-05-28 Pompe a piston Expired - Lifetime EP0862693B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19635164A DE19635164A1 (de) 1996-08-30 1996-08-30 Kolbenpumpe
DE19635164 1996-08-30
PCT/DE1997/001076 WO1998009075A1 (fr) 1996-08-30 1997-05-28 Pompe a piston

Publications (2)

Publication Number Publication Date
EP0862693A1 true EP0862693A1 (fr) 1998-09-09
EP0862693B1 EP0862693B1 (fr) 2002-08-07

Family

ID=7804162

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97925877A Expired - Lifetime EP0862693B1 (fr) 1996-08-30 1997-05-28 Pompe a piston

Country Status (6)

Country Link
US (1) US5937734A (fr)
EP (1) EP0862693B1 (fr)
JP (1) JPH11514722A (fr)
KR (1) KR19990067162A (fr)
DE (2) DE19635164A1 (fr)
WO (1) WO1998009075A1 (fr)

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DE19836901C2 (de) * 1998-08-14 2002-08-29 Bosch Gmbh Robert Radialkolbenpumpe
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DE10115856C1 (de) * 2001-03-30 2002-08-08 Bosch Gmbh Robert Hochdruck-Kraftstoffpumpe für eine direkteinspritzende Brennkraftmaschine, Kraftstoffsystem für eine direkteinspritzende Brennkraftmaschine, sowie direkteinspritzende Brennkraftmaschine
DE10140918A1 (de) * 2001-05-28 2002-12-05 Continental Teves Ag & Co Ohg Motor-Pumpen-Aggregat, insbesondere für ein Kraftfahrzeugbremssystem
DE10212492B4 (de) 2002-03-21 2012-02-02 Daimler Ag Kolbenpumpe
DE10249818B4 (de) * 2002-10-24 2005-10-20 Daimler Chrysler Ag Oberfläche eines Körpers, auf dem ein anderer Körper in einer bevorzugten Gleitrichtung gegeneinander gleitend anordenbar ist
DE10256525A1 (de) * 2002-12-04 2004-06-24 Robert Bosch Gmbh Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE10256528A1 (de) * 2002-12-04 2004-06-24 Robert Bosch Gmbh Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE10326863A1 (de) * 2003-06-14 2004-12-30 Daimlerchrysler Ag Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen
DE20313014U1 (de) * 2003-08-21 2004-12-23 Robert Bosch Gmbh Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
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EP2050952A1 (fr) * 2007-10-16 2009-04-22 Delphi Technologies, Inc. Pompe à carburant
DE102007052664A1 (de) * 2007-11-05 2009-05-07 Robert Bosch Gmbh Führungsring für eine Kolbenpumpe sowie Kolbenpumpe
DE102007055263A1 (de) 2007-11-20 2009-05-28 Robert Bosch Gmbh Vierzylinder-Hochdruckkraftstoffpumpe
DE102007062181A1 (de) 2007-12-21 2009-06-25 Robert Bosch Gmbh Hochdruckkraftstoffpumpe
DE102007062179A1 (de) 2007-12-21 2009-06-25 Robert Bosch Gmbh Hochdruckkraftstoffpumpe mit variablen Kolbenhub
ITMI20080431A1 (it) * 2008-03-13 2009-09-14 Bosch Gmbh Robert Pompa di alta pressione per alimentare combustibile a un motore a combustione interna
JP5275015B2 (ja) * 2008-12-24 2013-08-28 カヤバ工業株式会社 車高調整装置
CN102026835B (zh) * 2008-12-24 2013-08-21 萱场工业株式会社 车高调整装置
JP5275014B2 (ja) * 2008-12-24 2013-08-28 カヤバ工業株式会社 車高調整装置
DE202009003133U1 (de) * 2009-03-09 2009-06-04 Baudat Gmbh & Co. Kg Kolbenpumpe mit mehreren Kolben
ITMI20090606A1 (it) * 2009-04-14 2010-10-15 Bosch Gmbh Robert Pompa a pistoni per alimentare combustibile, preferibilmente gasolio, a un motore a combustione interna e metodo di accoppiamento di un albero della stessa con le rispettive sedi di rotazione
DE102010042295A1 (de) * 2010-10-12 2012-04-12 Robert Bosch Gmbh Hochdruckpumpe und Triebwerk für eine Hochdruckpumpe
DE102010064053A1 (de) * 2010-12-23 2012-06-28 Robert Bosch Gmbh Exzenterantrieb für mindestens einen kolben einer Kolbenpumpe
WO2014203962A1 (fr) * 2013-06-21 2014-12-24 株式会社リベックス Pompe hydraulique à pistons radiaux
JP2016223298A (ja) * 2015-05-27 2016-12-28 日立オートモティブシステムズ株式会社 ピストンポンプまたはブレーキ装置用ポンプ
JP6741199B2 (ja) * 2016-10-12 2020-08-19 日立オートモティブシステムズ株式会社 ポンプ装置及びブレーキ装置
CN111594408B (zh) * 2020-05-12 2022-05-31 合肥通用机械研究院有限公司 一种凸轮式往复压缩机构
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

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Also Published As

Publication number Publication date
DE19635164A1 (de) 1998-03-05
EP0862693B1 (fr) 2002-08-07
US5937734A (en) 1999-08-17
KR19990067162A (ko) 1999-08-16
JPH11514722A (ja) 1999-12-14
DE59707915D1 (de) 2002-09-12
WO1998009075A1 (fr) 1998-03-05

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