EP1672215B1 - Pompe hydraulique à pistons - Google Patents

Pompe hydraulique à pistons Download PDF

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Publication number
EP1672215B1
EP1672215B1 EP05024333A EP05024333A EP1672215B1 EP 1672215 B1 EP1672215 B1 EP 1672215B1 EP 05024333 A EP05024333 A EP 05024333A EP 05024333 A EP05024333 A EP 05024333A EP 1672215 B1 EP1672215 B1 EP 1672215B1
Authority
EP
European Patent Office
Prior art keywords
piston
pressure
machine according
valve
piston machine
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.)
Not-in-force
Application number
EP05024333A
Other languages
German (de)
English (en)
Other versions
EP1672215A3 (fr
EP1672215A2 (fr
Inventor
Brian J. Kane
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.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
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 Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1672215A2 publication Critical patent/EP1672215A2/fr
Publication of EP1672215A3 publication Critical patent/EP1672215A3/fr
Application granted granted Critical
Publication of EP1672215B1 publication Critical patent/EP1672215B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F04B53/125—Reciprocating valves
    • F04B53/129—Poppet valves
    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/18—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having self-acting distribution members, i.e. actuated by working fluid
    • F04B1/182—Check valves

Definitions

  • the invention relates to a hydraulic piston engine according to the preamble of patent claim 1.
  • Such hydraulic piston machines are designed for example as a radial or axial piston machine.
  • a double-swashplate machine in which a plurality of pistons are accommodated in a fixed drum, which are guided in pairs in opposite directions in the drum.
  • the axial displacement of the counter-rotating piston via two arranged on both sides of the drum swash plates, which are rotatably connected to a drive shaft.
  • Each piston is supported via a sliding block on its associated swash plate, said piston and the piston are penetrated by a pressure equalization bore, is guided over the pressure medium to the sliding surface of the shoe, so that it is hydrostatically supported.
  • the pressure medium supply and pressure fluid discharge takes place via suction and pressure valves, which are designed as a slide whose slide sleeves are guided on the outer circumference of the piston and in the cylinder.
  • the DE 27 16 888 C3 discloses a radial piston pump, wherein the pistons are arranged in the radial direction about an eccentric shaft. In this solution, the suction valves are integrated into the piston, but there is no hydrostatic bearing of the shoes.
  • a generic piston engine which is designed as an axial piston pump with swash plate.
  • the suction valves are arranged on the working chambers facing the end portions of the pistons.
  • the pressure equalization takes place via a throttle bore, which passes through the piston and which produces a pressure fluid connection from the working space to the voltage applied to the swash plate sliding surface of the respective sliding shoe.
  • a disadvantage of this solution is that the production of the piston is very expensive, since they are designed with a plurality of inner holes and further must be formed to guide the closing body of the suction valve, a radially recessed piston projection.
  • Another disadvantage of this known solution is that this axial projection always dips axially into the working space with the closing body guided thereon and correspondingly increases the overall length of the pump.
  • the invention has for its object to provide a hydraulic piston machine that is compact and easy to manufacture.
  • the hydraulic piston engine has a multiplicity of pistons displaceably guided in a cylinder, each defining a working space.
  • This is inventively formed by a capillary tube which is inserted into the piston.
  • This capillary tube is less susceptible to dirt because it has no radial shoulders and, moreover, the diameter of the capillary tube is larger than that part of the prior art stepped bore over which the nozzle of the pressure compensating pressure fluid flow path is formed.
  • the production of this piston is particularly simple, since only the receiving bore for the capillary tube must be made as a through hole and this is then inserted into the receiving bore.
  • the suction valve is inserted into a space on the working space side end portion, so that the axial length is minimal.
  • the closing body of the suction valve is preferably designed as a cone, which against a on Inner circumference of the piston formed valve seat is biased.
  • the closing body of the suction valve is displaceably guided in the piston and along the capillary tube.
  • the weight of the piston engine can be minimized if the pistons and also the suction valve closing bodies integrated in them are made of a wear-resistant plastic, for example PEEK.
  • the capillary tube is preferably designed as a metal tube and is extended at its working-side end portion in the radial direction to a support portion on which a closing spring of the suction valve is supported.
  • the radially expanded region can be formed, for example, by crimping.
  • the piston foot via a sliding shoe on a helical or swash plate.
  • the piston engine is designed as a double swashplate machine or Doppelschrägkolben-machine, so that the axial forces are balanced.
  • the weight of the piston engine can be further reduced even if the closing body of the pressure valves are made of plastic.
  • FIG. 1 a double swashplate pump 1 is shown in longitudinal section.
  • a pump 1 has a rotatably received in a housing 2 cylinder 4, which is traversed axially parallel with a plurality of lying on a common pitch cylinder bores 6. These open in each case in the end faces of the cylinder 4 and each receive two oppositely movable pistons 8, 10. These protrude with a piston foot 12, 14 out of the respective end face of the cylinder 4.
  • the piston 12, 14 is spherical and carries a shoe 16, 18. About these shoes 16 are in FIG. 1 from the right end face of the cylinder 4 projecting piston 10 on a first swash plate 20 and the sliding shoes 18 from the left end face (perpendicular to the plane in FIG FIG.
  • the two swash plates 20, 22 are each arranged in a suction chamber 28, 30, which each open into a suction port 32, 34, which is connected to a tank or the like.
  • a working space 36 is limited in the axial direction, which increases by the opposite piston movement during the suction stroke and reduced during the compression stroke.
  • the pressurized pressure medium is conveyed in the illustrated embodiment via a respectively a working space 36 associated, arranged radially in the housing 4 pressure valve 38 and a pressure port 40 to the connected consumer.
  • the pressure fluid connection between the working chamber 36 and the suction chamber 28, 30 is controlled via a respective suction valve 42, 44, the closing body - as explained in more detail below - in the associated piston 8, 10, is mounted.
  • each working space two suction valves 42, 44 and a pressure valve 38 are assigned.
  • retraction plate 46, 48 can be removed, which are applied to each swash plate 20, 22 sliding blocks 12 via a retraction plate 46, 48 are positioned relative to each other.
  • These retraction plates 46, 48 are supported on a counter bearing 50, 52, which is biased by a central clamping device 54 in the direction of the respective adjacent swash plate 20, 22, so that the sliding blocks 16, 18 do not lift off the associated swash plate 20, 22 during the suction stroke.
  • FIG. 2 shows a schematic partial representation of the swash plate pump 1 FIG. 1 with the two received in a cylinder bore 6 piston 8, 10 the common pressure valve 38 and the two suction valves 42, 44, wherein these are shown in their inner dead center, while FIG. 1 shows a position just before the inner dead center.
  • Each piston 8, 10 has an approximately cylindrical piston skirt 56, which merges via a constriction 58 in the spherical piston 14 (the pistons of the other side are identically constructed, so that a separate description is omitted). This is in ball-joint-like engagement with the associated shoe 18, which in turn rests with its sliding surface 60 on the end face of the swash plate 22.
  • a pressure medium flow path 22 which opens on the one hand in the working space 36 and on the other hand in the sliding surface 60.
  • This pressure compensating pressure medium flow path is usually provided with a nozzle to dampen the pressure fluctuations during the working cycle.
  • this nozzle usually formed by an inner shoulder of the piston is dispensed with and instead a continuous capillary tube 64 is used, which is based on FIG. 3 will be explained in more detail.
  • the pressure chamber 30 is connected via oblique bores 66 of the constriction portion 58 with a gripped by the cylindrical portion 56 of the piston 10 space 68.
  • FIG. 3 shows an enlarged view of the area in which the valve control with the suction valves 42, 44 and the pressure valve 38 are received.
  • a valve seat 70 is formed on the inner, the receiving space 36 facing annular end face of each piston 8, 10, against which a closing body 72 of the suction valve 42, 44 is biased with its closing cone.
  • longitudinal grooves 76 are formed, via the pressure medium from the space 68 to the valve seat 70, can pass.
  • the maximum outer circumference of the cylindrical part 74 of the closing body 72 corresponds to the diameter of the inner circumferential wall of the space 68, so that the closing body is slidably guided along the inner circumferential wall radially bounding the space 68.
  • the closing cone of the closing body 72 extends somewhat into the working space 36, but the maximum outside diameter of the closing cone is chosen to be slightly smaller than the diameter of the cylinder bore 6, so that the closing body 72 can dip into the cylinder bore 6 during the suction stroke.
  • the closing body 72 is with its closing cone by means of a closing spring 80 (see also FIG. 1 ), which is supported on a radially projecting abutment shoulder 82 of the capillary tube 64 and engages an inner shoulder 84 of the closing body 72.
  • the capillary tube 64 is made of metal, wherein the abutment shoulder 82 can be formed for example by crimping.
  • the outer diameter of this abutment shoulder 82 is chosen so that it at the inner dead center ( FIG.
  • FIG. 3 shows the capillary tube 64 passes through the closing body, so that it is slidably guided on the capillary tube 68 and this also protects against lateral buckling.
  • the closing body 72 of the suction valves 42, 44, the piston 8, 10 and the sliding blocks 16, 18 are made of fiber-reinforced plastic, preferably carbon fiber reinforced PEEK. These components are preferably produced by injection molding, wherein the sliding blocks 16, 18 can be molded directly to the associated piston 8, 10. This is described in the parallel filed application of the applicant (title: piston arrangement).
  • the valve body 86 of the common pressure valve 38 is made of plastic, so that the double swashplate pump 1 is designed with minimal weight and minimal moving masses.
  • the suction valves 42, 44 are respectively disposed at the inner end portion of the working piston 8, 10, so that the dead volume is reduced compared to solutions in which the suction valves are provided in the region of the piston foot.
  • the inner diameter of the capillary tubes 64 used is chosen so that the hydrostatic support of the sliding shoes 18 is ensured during the suction and compression stroke.
  • the constant capillary diameter and the smooth walls of the capillary tube 64 provide no attachment surfaces for contamination of the pressure medium, so that this pressure fluid flow path 62 is always open. In the conventional solutions, soiling can attach relatively easily to the necessary for the formation of the nozzle inner stages.
  • the capillary tube 64 ends in a funnel-shaped extension 87 of the pressure medium flow path 92.
  • This extension 87 is required in order to maintain the pressure medium connection to the sliding surface 60 even during the in FIG. 2 shown Relativverschwenkung between shoe 18 and piston 10 maintain.
  • the capillary tube 64 has according to the above embodiments, a dual function, on the one hand it forms the pressure fluid flow path 62 and has a throttling effect to compensate for pressure fluctuations, on the other hand it acts as Ventilhubbegrenzung for the closing body 72, which then with its inner shoulder 84 on the abutment shoulder 82 on inner end of the capillary tube 68 runs and thus can not be moved axially.
  • the pressure valve 38 is arranged in a radially extending through the housing 2 and the cylinder 4 pressure channel 88. This has a radial shoulder, which forms a valve seat 90, against which the plate-shaped valve body 86 is biased by a closing spring assembly 92 so that a return flow is prevented by a common pressure connection to the working space 36.
  • a closing spring assembly 92 The construction of such plate-shaped valves is known, so that further explanations are unnecessary.
  • valve control over the conventional constructions with a control plate is that the volumetric efficiency can be improved by eliminating the end control plates and the concomitant reduction of leakage losses. Furthermore, the friction forces are reduced by eliminating the control plate.
  • the relatively soft switching valve elements allow noise reduction and minimizing the dead volume.
  • the above double swashplate pump 1 can be operated without conversion in both directions of rotation, wherein the inventive design with pistons made of plastic 8, 10, valve body 86 and closing body 72 and sliding shoes 16, 18 Die Making the pump simplified, since these components virtually no reworking is required.
  • FIG. 4 shows a variant of the basis of the FIGS. 1 to 3 explained concept.
  • the working space is subdivided by a thrust washer 94 inserted into the cylinder into two sub-work spaces 36a, 36b, to each of which a pressure valve 38a, 38b is assigned.
  • Each pressure valve 38a, 38b has a valve body 86a, 86b biased against valve seats 90a, 90b by a common closing spring assembly 92.
  • the pressure channel 88 then extends as in the above-described embodiment in the radial direction through the cylinder 4 and the housing 2 through to the common pressure port.
  • FIG. 4 illustrated embodiment differs essentially in that each piston 8, 10 a separate working space 36a, 36b is assigned and that the corresponding pressure valves 38a, 38b open not in the radial direction but in the axial direction.
  • the high-pressure valves of the above-described solutions can be switched out of phase by suitable design in order to achieve a minimization of the pressure pulsation.
  • FIG. 5 shows an embodiment in which the working machine is designed as Einommentaumelpumpe, wherein in the cylinder 4, only the pistons 10 are guided axially displaceable and abut on the sliding blocks 18 on the single swash plate 22.
  • the housing 2 is one-sided with compressive forces acted, advantage is, however, that the pump 1 builds shorter in the axial direction.
  • the valve control is like the in FIG. 4 illustrated embodiment designed. Accordingly, the suction valves 44 are integrated into the respective pistons 10, the pressure chamber 38 connecting the working chamber 36 with the radial pressure channel 88 is arranged in the axial direction, the closing spring arrangement 92 being supported on the housing 2.
  • the suction valves 44 are integrated into the respective pistons 10
  • the pressure chamber 38 connecting the working chamber 36 with the radial pressure channel 88 is arranged in the axial direction
  • the closing spring arrangement 92 being supported on the housing 2.
  • a hydraulic piston engine in particular a Doppelaumelinnpumpe, with a plurality of pistons, which are guided displaceably in a cylinder, and each defining a working space in the pressure medium via a suction valve can be supplied and discharged from the pressure medium via a pressure valve.
  • the piston is penetrated by a pressure-compensating pressure medium flow path, which is formed according to the invention by a capillary tube inserted into the piston.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)

Claims (12)

  1. Pompe hydraulique à pistons, comportant une pluralité de pistons (8, 10), qui sont logés de manière mobile dans un cylindre (4) et qui délimitent respectivement une chambre de travail (36), dans laquelle peut être acheminé un fluide sous pression en passant par un clapet d'aspiration (42, 44) disposé sur le piston (8, 10) et hors de laquelle le fluide sous pression peut être refoulé en passant par un clapet de refoulement (38), le piston (8, 10) étant traversé par une voie d'écoulement du fluide sous pression (62) pour l'équilibrage de la pression, caractérisée en ce que la voie d'écoulement du fluide sous pression (62) est délimitée au moins par tronçons par un tube capillaire (64) incorporé dans le piston (8, 10).
  2. Pompe à pistons selon la revendication 1, dans laquelle le clapet d'aspiration (42, 44) est inséré dans un espace (68) d'une zone d'extrémité, du côté chambre de travail, du piston (8, 10).
  3. Pompe à pistons selon la revendication 2, dans laquelle une bille d'un corps de fermeture (72) du clapet d'aspiration (42, 44) est en appui sur un siège de clapet (70) réalisé sur le pourtour intérieur du piston (8, 10).
  4. Pompe à pistons selon la revendication 2 ou 3, dans laquelle le corps de fermeture (72) est logé dans le piston (8, 10) et/ou au niveau du tube capillaire (64).
  5. Pompe à pistons selon l'une quelconque des revendications précédentes, dans laquelle le corps de fermeture (72) et le piston (8, 10) sont réalisés en matière plastique renforcée par fibres.
  6. Pompe à pistons selon l'une quelconque des revendications précédentes, dans laquelle le tube capillaire (64) est réalisé en métal.
  7. Pompe à pistons selon l'une quelconque des revendications précédentes, dans laquelle un ressort de fermeture (80) du clapet d'aspiration (42, 44) est en appui sur le tube capillaire (64).
  8. Pompe à pistons selon la revendication 7, dans laquelle le ressort de fermeture (80) est en appui sur une zone (82) élargie radialement du tube capillaire (64).
  9. Pompe à pistons selon la revendication 8, dans laquelle la zone (82) élargie est réalisée par sertissage.
  10. Pompe à pistons selon l'une quelconque des revendications précédentes, dans laquelle un pied de piston (12, 14) est en appui par l'intermédiaire d'un patin (16, 18) sur un plateau biais ou plateau oscillant (20, 22).
  11. Pompe à pistons selon la revendication 10, dans laquelle des pistons (8, 10), disposés en sens opposé, sont logés dans le cylindre (4), deux plateaux biais ou plateaux oscillants (20, 22), disposés sur les deux côtés du cylindre (4), étant associés auxdits pistons.
  12. Pompe à pistons selon l'une quelconque des revendications précédentes, dans laquelle le clapet de refoulement (38) est disposé dans le cylindre (4) ou dans le carter (2) de la pompe, le corps (86) dudit clapet de refoulement étant réalisé également en matière plastique renforcée par fibres.
EP05024333A 2004-12-17 2005-11-08 Pompe hydraulique à pistons Not-in-force EP1672215B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102004060954A DE102004060954A1 (de) 2004-12-17 2004-12-17 Hydraulische Kolbenmaschine

Publications (3)

Publication Number Publication Date
EP1672215A2 EP1672215A2 (fr) 2006-06-21
EP1672215A3 EP1672215A3 (fr) 2008-03-12
EP1672215B1 true EP1672215B1 (fr) 2009-05-13

Family

ID=36121502

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05024333A Not-in-force EP1672215B1 (fr) 2004-12-17 2005-11-08 Pompe hydraulique à pistons

Country Status (3)

Country Link
EP (1) EP1672215B1 (fr)
AT (1) ATE431503T1 (fr)
DE (2) DE102004060954A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104100486A (zh) * 2014-06-30 2014-10-15 华中科技大学 一种轴向柱塞式电机泵

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007001793A1 (de) 2007-01-05 2008-07-10 Robert Bosch Gmbh Hydraulische Kolbenmaschine
DE102007001794A1 (de) 2007-01-05 2008-07-10 Robert Bosch Gmbh Hydraulische Kolbenmaschine
DE102011114093B4 (de) 2011-09-21 2013-06-06 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Umkehrosmose-Anlage und deren Verwendung enthaltend einen aktiven Druckintensivierer
DE102012013436A1 (de) 2012-06-01 2013-12-05 Robert Bosch Gmbh Hydraulische Kolbenmaschine und hydraulische Maschine
CN111997858A (zh) * 2020-09-10 2020-11-27 芜湖西南机械有限公司 变量柱塞泵的结构组成及其控制方法

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3183848A (en) 1962-05-09 1965-05-18 Hydro Kinetics Inc Cartridge type pumping apparatus
US3514223A (en) 1968-08-19 1970-05-26 Applied Power Ind Inc Hydraulic pump
DE2716888C3 (de) 1977-04-16 1985-08-22 Mannesmann Rexroth GmbH, 8770 Lohr Hydrostatische Radialkolbenpumpe
ES2085120T3 (es) 1992-02-28 1996-05-16 Leduc Rene Hydro Sa Bomba hidraulica de pistones provistos de valvulas de aspiracion.
PL173937B1 (pl) 1994-07-12 1998-05-29 Andrzej Osiecki Maszyna hydrostatyczna wielotłoczkowa osiowa

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104100486A (zh) * 2014-06-30 2014-10-15 华中科技大学 一种轴向柱塞式电机泵
CN104100486B (zh) * 2014-06-30 2016-06-22 华中科技大学 一种轴向柱塞式电机泵

Also Published As

Publication number Publication date
ATE431503T1 (de) 2009-05-15
DE502005007268D1 (de) 2009-06-25
EP1672215A3 (fr) 2008-03-12
DE102004060954A1 (de) 2006-06-29
EP1672215A2 (fr) 2006-06-21

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