EP1156212B1 - Machine à piston alternatif axial avec des chemises de cylindre pour les pistons - Google Patents

Machine à piston alternatif axial avec des chemises de cylindre pour les pistons Download PDF

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Publication number
EP1156212B1
EP1156212B1 EP20010102330 EP01102330A EP1156212B1 EP 1156212 B1 EP1156212 B1 EP 1156212B1 EP 20010102330 EP20010102330 EP 20010102330 EP 01102330 A EP01102330 A EP 01102330A EP 1156212 B1 EP1156212 B1 EP 1156212B1
Authority
EP
European Patent Office
Prior art keywords
piston engine
axial piston
cross
engine according
piston
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
EP20010102330
Other languages
German (de)
English (en)
Other versions
EP1156212A2 (fr
EP1156212A3 (fr
Inventor
Reinhold Schniederjan
Herbert Kurz
Werner Hörmann
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik 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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1156212A2 publication Critical patent/EP1156212A2/fr
Publication of EP1156212A3 publication Critical patent/EP1156212A3/fr
Application granted granted Critical
Publication of EP1156212B1 publication Critical patent/EP1156212B1/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
    • F04B1/12—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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—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
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/166—Cylinder liners

Definitions

  • the invention relates to an axial piston machine according to the preamble of claim 1.
  • a piston pump which is provided in particular for a hydraulic, slip-controlled vehicle brake system.
  • the document proposes to install a displacement body by means of a holding part on the piston, which protrudes into an interior of a coil spring formed as a closing spring of a valve integrated in the piston.
  • the formation of the valve closing spring and a piston return spring with a rectangular winding cross section serves to reduce the dead space of the piston pump. The reduction of the dead space increases the efficiency of the piston pump.
  • a method of mounting a bush in a body of a hydraulic machine and a hydraulic machine are known.
  • a method of mounting a bushing in a body of a hydraulic machine wherein the bushing is inserted into a cylinder bore provided with a groove in the inner wall, and a hydraulic machine.
  • materials for the liner can be used, which are not or only with difficulty deformable.
  • a groove is produced on the outer wall of the bushing, the bushing is inserted so far into the body, that the inner wall groove and the outer wall groove at least partially overlap, and a locking element is at least positively in a through the inner wall groove and introduced groove space formed the outer wall groove.
  • a piston engine of this type is described in the form of a swash plate axial piston machine.
  • a cylinder drum for a hydrostatic piston machine is described, are arranged in the guide bushes in the socket holes, wherein the length of the guide bushes corresponds to the length of the bushing holes.
  • the invention has for its object to design a piston engine or a guide bush of the types described above so that the risk of axial displacement of the guide bush is reduced during operation.
  • each of the inner circumferential surface of the guide bush in the region of its head end on a cross-sectional enlargement acts with radially outwardly directed compressive forces against the inner wall of the cross-sectional widening, wherein the compressive forces spread the cross-sectional widening longitudinal portion of the guide bush and press against the inner wall of the associated bushing hole.
  • a radially effective clamping force between the tapered longitudinal portion of the guide bush and the inner wall of the bushing hole is generated, which consolidates or stabilizes the seat of the guide bush in the bushing hole. This is done in the function mode automatically by the working pressure in the associated working chambers.
  • the spreading of the guide bush is thus laid in a part of the guide bush, which does not touch the piston.
  • the inventive design thus does not lead to an increase in the friction between the piston and the Guide bushing and not to additional resulting from the friction axial forces.
  • the embodiments of the invention are advantageous not only because of the achievable stabilization of the seat of the guide bush in the socket hole. It should also be noted that the achievable by the inventive design stabilization of the seat takes place only in functional operation, d. H. at standstill of the piston engine, the seat stabilizing clamping action does not occur. Consequently, the bushing is seated during the stoppage of the piston engine with a smaller interference fit in the bushing hole, and it can therefore be pulled out with smaller axial forces from the bushing, z. B. in order to replace the liner during a repair. In addition, the guide bushing according to the invention can be more easily pressed into the bushing hole due to the lower interference fit.
  • cross-sectional widening with a hollow cylindrical inner circumferential surface, whereby not only a simple configuration is achieved but is loaded in the spread of the cross-sectional widening having longitudinal section of this with uniform or even stresses.
  • the cross-sectional widening limiting step surface of the liner may be formed radially, conically or concave rounded.
  • the achievable by the inventive design in functional operation clamping force is greater, the longer the cross-sectional widening having longitudinal portion of the guide bushing. Ie. it is advantageous to form and arrange the tapered longitudinal portion of the guide bush so that it extends to the Vorhubend ein of the piston or extends beyond.
  • the exemplary and designated in its entirety by 1 piston engine has a housing 2, in the interior of which 3 a swash plate 4 and a cylinder drum 5 are arranged side by side.
  • the cylinder drum 5 distributed on the circumference bushing holes 6 are arranged, which in the present embodiment of an axial piston machine substantially parallel to a Center axis 7 of the cylinder drum 5 extend and at the swashplate 4 facing end face 5a of the cylinder drum 5 are open.
  • guide bushes 8 are firmly inserted, preferably pressed, between the preferably cylindrical outer circumferential surfaces 8a and inner circumferential surfaces 6a of the female holes 6 is a certain excess, whereby a press fit is ensured.
  • the guide bushings 8 can end on the swashplate facing end face 5 a of the cylinder barrel 5.
  • preferably cylindrical piston 9 are mounted substantially axially displaceable, which limit 9a with their piston heads working chambers 11 in the cylinder drum 5 in the direction of the swash plate 4.
  • the swash plate 4 facing the foot ends 9b of the piston 9 are each supported by a hinge 12 on the swash plate 4, wherein sliding shoes 13 may be present, between which and the foot ends 9b which are preferably designed as ball joints with a ball head and a ball recess joints 12 are arranged ,
  • the cylinder drum 5 is located with its side facing away from the swash plate 4 5b on a control disk 14, in which two control openings 15 are arranged in the form of through holes which form sections of an indicated supply line 16 and a discharge line 17 extending through an adjacent housing wall 18th extend, on which the control disk 14 is held.
  • the cylinder drum 5 is mounted on a drive shaft 19, which is rotatably mounted in the housing 2 and whose axis of rotation 21 is coaxial with the central axis 7.
  • the housing 2 from a cup-shaped housing part 2a with a housing bottom 2b and a peripheral wall 2c and a housing wall 18 forming cover 2d formed which rests against the free edge of the peripheral wall 2c and thus screwed by suggestively illustrated screws 22.
  • cover 2d formed which rests against the free edge of the peripheral wall 2c and thus screwed by suggestively illustrated screws 22.
  • 17 2d line connections 16a, 17a are provided on the lid.
  • the drive shaft 19, which passes through the cylinder drum 5 in a bearing bore 23 is rotatably supported and sealed in bearing recesses of the housing base 2b and the cover 2d by means of suitable bearings 25, 26, in particular rolling bearings, wherein the housing bottom 2b passes axially through and with a drive pin 19a protrudes from the housing base 2b.
  • the cylinder drum 5 by a rotary driving connection 26, z.
  • a toothed coupling rotatably mounted on the drive shaft 19, which passes through the firmly arranged on the housing bottom 2 or formed therein swash plate 4 in a through hole 27.
  • the cylinder drum 5 rotates in the functional operation, the cylinder drum 5 relative to the swash plate 4, wherein the pistons 9 are moved longitudinally in the direction of the working chambers 11 and back.
  • a retraction device known per se here with a flanges of the sliding blocks 13 inside and resting on a spherical segment thrust bearing 29 of the drive shaft 19 supporting retraction disc 31, the retraction movement is made possible.
  • the guide bushes 8 in their the openings 6b of the socket holes 6 facing away from the end regions a to a terminal expiring cross-sectional enlargement 32 of its inner circumferential surface 8b, whereby the thickness d of the guide bushes 8 is reduced in the region of the cross-sectional widening 32.
  • the cross-sectional widening 32 is bounded by its preferably hollow cylindrical inner lateral surface 32a in the direction of the associated opening 6b by a step surface 32b, which preferably extends conically or radially, but may also be concavely rounded in order to stabilize the existing groove.
  • the radially outwardly directed spreading forces 33 counteract in the working chambers 11 adjacent end portion of the respective guide bushing 8 effective and radially inwardly directed contraction forces 35, but the latter are smaller, in particular with increasing distance from the opening 6b facing away from the head 8c of the guide bush 8.
  • These contraction forces 35 are generated by the hardly avoidable pressure effect of the hydraulic medium in the joint between the guide bushing 8 and the inner circumferential surface 6a.
  • the spreading forces 33 are supported by additional also radially outwardly directed spreading forces 36, which are generated by the present in the joint between the piston 9 and guide bushing 8 pressure, and which are also smaller with increasing distance from the head end 8c.
  • the step surface 32b is preferably arranged in such a position that in the remindhubend ein the head ends 9a of the piston 9 are in the region of the step surface 32b or project beyond this.
  • Fig. 1 to 3 is the axial length of the extended end portion a dimensioned larger than in the embodiment according to Fig. 4 in which the same or comparable parts are provided with the same reference numerals.
  • the extended end region a can be dimensioned equal to or greater than about the inner or outer cross-sectional dimension of the guide bushing 8, extending to about the Vorhubend ein of the piston 9 or beyond the end facing away from the opening 6b or in the vicinity of the bushing hole 6 can. With increasing length of the cross-sectional widening 32 or of the tapered end region a, the radial spreading force for securing the guide bush 8 in the bushing hole 6 is increased.
  • the length of the cross-sectional widening 32 need only be a few mm. Their length can be z. B. correspond approximately to the thickness d of the guide bushing 8.
  • a spiral groove 38 in the region of the guide bushes 8 facing the opening 6b in its outer circumferential surface 8a, specifically in a longitudinal region which terminates at a distance from the head end 8c or from the annular groove 37.
  • the spiral groove 37 extends into the annular groove 37.
  • the axial length c may be a few mm.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Claims (7)

  1. Machine à pistons axiaux (1) comprenant un plateau incliné (4) et un tambour ou barillet de cylindres (5) dans lequel plusieurs pistons (9), agencés de manière répartie sur un périmètre, sont guidés en coulissement dans des chemises de guidage (8), les chemises de guidage (8) étant insérées, avec leurs extrémités de tête (8c), dans des alésages de chemise (6) du tambour à cylindres (5), et y étant fixées, et les pistons (9) délimitant, avec leurs extrémités de tête (9a), des chambres de travail (11) dans le tambour de cylindres (5), et s'appuyant, avec leurs extrémités de base (9b), sur une pièce motrice de la machine à pistons (1),
    caractérisée
    en ce que les surfaces périphériques intérieures (8b) des chemises de guidage (8) présentent chacune respectivement, au niveau des zones terminales (a) de leurs extrémités de tête (8c), un élargissement de section transversale (32).
  2. Machine à pistons axiaux selon la revendication 1,
    caractérisée
    en ce que l'élargissement de section transversale (32) débouche axialement au niveau de l'extrémité de tête (8c) considérée de la chemise de guidage (8).
  3. Machine à pistons axiaux selon la revendication 1 ou la revendication 2,
    caractérisée
    en ce que l'élargissement de section transversale (32) est limité axialement par une surface de gradin (32b), qui est d'une configuration radiale ou conique, ou bien d'une configuration arrondie, concave.
  4. Machine à pistons axiaux selon l'une des revendications 1 à 3,
    caractérisée
    en ce que la surface périphérique intérieure (32a) de l'élargissement de section transversale (32) est une surface cylindrique creuse.
  5. Machine à pistons axiaux selon l'une des revendications précédentes,
    caractérisée
    en ce que la longueur axiale (a) de la zone terminale correspond au moins environ à l'épaisseur (d) de la chemise de guidage (8).
  6. Machine à pistons axiaux selon l'une des revendications précédentes,
    caractérisée
    en ce que dans la position terminale de la course de retour des pistons (9), leur extrémité de tête (9a) se trouve dans la zone de l'extrémité arrière respective de l'élargissement de section transversale (32), ou dépasse de cette extrémité arrière.
  7. Machine à pistons axiaux selon l'une des revendications précédentes,
    caractérisée
    en ce que dans la surface périphérique extérieure (8a) de chacune des chemises de guidage (8) est agencée une rainure annulaire (37), à une distance (b) de l'extrémité de tête (8c).
EP20010102330 2000-05-16 2001-02-01 Machine à piston alternatif axial avec des chemises de cylindre pour les pistons Expired - Lifetime EP1156212B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10023849 2000-05-16
DE2000123849 DE10023849B4 (de) 2000-05-16 2000-05-16 Kolbenmaschine mit in Führungsbuchsen einer Zylindertrommel verschiebbar gelagerten Kolben und Führungsbuchse für eine solche Kolbenmaschine

Publications (3)

Publication Number Publication Date
EP1156212A2 EP1156212A2 (fr) 2001-11-21
EP1156212A3 EP1156212A3 (fr) 2003-06-11
EP1156212B1 true EP1156212B1 (fr) 2010-04-28

Family

ID=7642179

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20010102330 Expired - Lifetime EP1156212B1 (fr) 2000-05-16 2001-02-01 Machine à piston alternatif axial avec des chemises de cylindre pour les pistons

Country Status (2)

Country Link
EP (1) EP1156212B1 (fr)
DE (2) DE10023849B4 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7073427B2 (en) 2001-09-19 2006-07-11 Brueninghaus Hydromatik Gmbh Hydrostatic machine with compensated sleeves
DE10220611A1 (de) * 2002-02-15 2003-08-28 Brueninghaus Hydromatik Gmbh Drehgleitlager
WO2013037611A1 (fr) 2011-09-15 2013-03-21 Robert Bosch Gmbh Manchon de guidage de piston pour une machine à piston axial, et machine à piston axial pourvue d'un manchon de guidage de piston
DE102014217143A1 (de) 2014-08-28 2016-03-03 Robert Bosch Gmbh Zylindertrommel für eine hydrostatische Axialkolbeneinheit
DE102018205010A1 (de) * 2018-04-04 2019-10-10 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2521182A1 (de) * 1975-05-13 1976-11-25 Kloeckner Werke Ag Schraegscheiben-axialkolbenmaschine
DE2812418A1 (de) * 1978-03-22 1979-10-04 Linde Ag Zylindertrommel fuer eine hydrostatische kolbenmaschine und verfahren zu deren herstellung
DE4029295A1 (de) * 1990-09-16 1992-03-19 Karl Eickmann Dichtung fuer hohe drucke
DE4301126C2 (de) * 1993-01-18 1995-05-24 Danfoss As Verfahren zum Montieren einer Laufbuchse in einem Grundkörper einer hydraulischen Maschine und hydraulische Maschine
GB9325388D0 (en) * 1993-12-11 1994-02-16 T M Kennedy & Co Ltd Apparatus for reciprocating pumps
JPH07180652A (ja) * 1993-12-24 1995-07-18 Tokimec Inc ピストン型液圧装置
DE4407978C2 (de) * 1994-03-10 2002-11-07 Continental Teves Ag & Co Ohg Kolbenpumpe
DE19521259C2 (de) * 1995-06-10 1998-11-05 Danfoss As Hydraulische Kolbenmaschine
DE19747850A1 (de) * 1997-07-30 1999-02-04 Bosch Gmbh Robert Kolbenpumpe

Also Published As

Publication number Publication date
EP1156212A2 (fr) 2001-11-21
DE10023849A1 (de) 2001-11-29
DE50115453D1 (de) 2010-06-10
DE10023849B4 (de) 2005-11-17
EP1156212A3 (fr) 2003-06-11

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