EP0921312B1 - Machine à pistons axiaux - Google Patents

Machine à pistons axiaux Download PDF

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Publication number
EP0921312B1
EP0921312B1 EP98121508A EP98121508A EP0921312B1 EP 0921312 B1 EP0921312 B1 EP 0921312B1 EP 98121508 A EP98121508 A EP 98121508A EP 98121508 A EP98121508 A EP 98121508A EP 0921312 B1 EP0921312 B1 EP 0921312B1
Authority
EP
European Patent Office
Prior art keywords
axial piston
piston machine
housing
machine according
pressure
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
EP98121508A
Other languages
German (de)
English (en)
Other versions
EP0921312A3 (fr
EP0921312A2 (fr
Inventor
Günter Wanschura
Rainer Stoelzer
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 EP0921312A2 publication Critical patent/EP0921312A2/fr
Publication of EP0921312A3 publication Critical patent/EP0921312A3/fr
Application granted granted Critical
Publication of EP0921312B1 publication Critical patent/EP0921312B1/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
    • F04B1/126—Piston shoe retaining means
    • 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
    • F04B53/22—Arrangements for enabling ready assembly or disassembly

Definitions

  • the invention relates to an axial piston machine according to the preamble of Claim 1.
  • the tappets due to the axial tensile force of the piston pushes outwards, causing the holding plungers to lose their stability and no or only can exert a reduced retention force on the perforated disc.
  • the perforated disc by the axial tensile force of the piston overused and z. B. is bent.
  • the tappets are particularly inclined, to dodge radially outwards. If, on the other hand, the inclination of the inclined surfaces is too small is, there is a risk that the holding plungers jam on the perforated disc, causing the Rotary operation would be impaired and due to wear with an insufficient Life would be expected.
  • Another major disadvantage of the known axial piston machine is that the mounting plungers due to their projection into the housing interior or Disassembly of the components located in the interior of the housing may be impaired.
  • the invention has for its object an axial piston machine of the beginning Specify the type specified so that while ensuring safe support of the Retraction device assembly or disassembly of those located in the interior of the housing Components are not affected by the restraint.
  • the retaining device is in the Functional operation of the axial piston machine automatically or automatically from a Retraction device release position in a the retraction device behind work position shifted and after switching off the functional mode automatically moved back to their release position, the shift into the Working position by printing from an existing, adjacent or neighboring Pressure chamber or a pressure line takes place and the shift to the release position done by the force of a spring.
  • an inherent pressure existing in the functional operation of the axial piston machine or an external pressure, e.g. B. from an adjacent axial piston machine can be in easily generate an insertion force that is greater than the required retraction or Pushing force, so that the position of the restraint in their working position is guaranteed.
  • the retraction device is in the area of the side half of the axial piston machine to arrange, in the area of which the pistons perform a suction stroke, this area extends approximately over 180 °.
  • One in the area of this side half, preferably centrally arranged retaining device, or several arranged on this side half Restraint devices are installed in one for pump operation
  • Axial piston machine also works when the axial piston machine is due to a braking function executes an engine operation.
  • adjustable axial piston machines are each one or more restraint devices to be arranged in the area of both side halves.
  • An advantageous embodiment for a restraint device is a cross section preferably circular stop pin, which is in a radial guide hole in the housing is slidably mounted between the working position and the release position. It is advantageous to provide the pin in its outer end region with a flange to which a spring arranged between the latter and an inner perforated shoulder, in particular a coil spring to attack and the stop pin in its release position can act.
  • a spring arranged between the latter and an inner perforated shoulder in particular a coil spring to attack and the stop pin in its release position can act.
  • For pneumatic or hydraulic displacement of the pin in its working position can be the one located radially outside with respect to the stop pin Hole space through a channel with the housing interior or with an inside Functional operation of the axial piston machine has an overpressure space be connected.
  • the channel can run in the housing wall or lengthways in the stop pin.
  • stop pin it is also advantageous to arrange the stop pin so that between it and the Retraction device is a small distance, which is only dimensioned so large that at overloading and deformation of the retraction device in its elastic range the retractor strikes the stop pin before it reaches its yield point is deformed out.
  • the drawing shows an axial partial section through an inventive Axial piston.
  • the main parts of those generally designated 1 Axial piston machines are a housing 2 with a section that is visible in the drawing Housing wall 2a, which encloses a housing interior 3, in which on a shaft 4 a cylinder drum 5 with several, preferably distributed on a pitch circle and lengthways Directed cylinder bores 6 are arranged, a plurality of pistons 7, which in the Cylinder bores 6 are axially displaceably mounted, a plurality of sliding shoes 8 pivotable, but axially fixed with spherical piston heads 9 at one end of the Pistons 7 are connected, a swash plate 11, on the inclined surface 12 the Sliding shoes 8 abut and are axially supported, the swash plate 11 by one perpendicular to the longitudinal center axis of the axial piston machine 1 or the axis of rotation 13 of the Shaft 4 extending pivot axis 14 in a pivot bearing, not shown is pivotally mounted and is locked in the
  • the retraction device 15 is through a perforated disc 22 in the number of 8 existing holes 23 formed, the edges of the holes in the sliding shoes Area surrounded by tapered glide heads with play and with their Swash plate 11 facing side on a foot flange 24 of the associated slide shoe 8 rest so that the foot flange 24 with little movement between the Inclined surface 12 and the perforated disc 22 is held.
  • the perforated disc 22 lies against it its side facing away from the swash plate 11 on a shoulder surface of the shaft 4 or Cylinder drum 5, whereby it faces away from the swash plate 11 Axis direction is supported.
  • the shoulder surface 25 can also be on a shaft 4 fixed support ring 26 may be formed.
  • a swiveling swash plate 11 is the shoulder surface 25 a spherical ring-shaped surface on which the perforated disc 22nd is supported with an inner support ring 27 which is tangential or concave spherical ring-shaped contact surface rests on the shoulder surface 25.
  • the retention device 16 is by a cylindrical or step-cylindrical Stop pin 31 formed, with little movement in a radial Guide hole or guide bore 32 radially displaceable in the housing wall 2a is mounted, the radial central axis 33 perpendicular to the axis of rotation 13 and parallel to Pivot axis 14 runs.
  • the stop pin 31 is between one radial inserted and shown in the drawing, in the radial position inner pin end 34 overlaps the outer edge of the perforated disk 22 and axially can support, and a radially extended release position in which the pin end 34 is pushed out of the housing interior or at least the perforated disc 22 without Cylinder drum 5 or the swash plate 11 for axial assembly or disassembly releases, adjustable.
  • the movements are limited by a stop 35.
  • the Working position is by a step surface 37 of the step-shaped Guide bore 32 and a step surface 38 of the radially outward divergent step trained stop pin 31 determined.
  • a plug 39 is in the outside incorporated guide hole 32 screwed in and sealed.
  • To seal the Stop pin 31 is one or two ring seals 41 are provided between the wall of the guide bore 32 and the outer surface of the stop pin 31 arranged in an annular groove on one or on both sides of the step surfaces 37, 38 and are effective.
  • the stop pin 31 is in its release position by the force of a spring 40 biased, which in the present embodiment is formed by a coil spring which engages and engages a flange 31a at the outer end of the stopper pin 31 a step surface 32a of an outer bore extension 32b of the guide bore 32 is applied.
  • a spring 40 biased which in the present embodiment is formed by a coil spring which engages and engages a flange 31a at the outer end of the stopper pin 31 a step surface 32a of an outer bore extension 32b of the guide bore 32 is applied.
  • the stop pin 31 is arranged so that between the retraction device 15, here the perforated disk 22, and the support surface 31b there is a small distance a which is at most so large that the retraction device 15 in the event of an overload hits the support surface 31b before the retraction device 15 beyond their elastic deformation range or beyond their yield strength is deformed. This ensures that the retraction device 15 only at Load peaks come into contact with the support surface 31b and then effectively over the Stop pin 31 is supported on the housing 2.
  • the overload stops return the retraction device 15 due to its elasticity back to its starting position back. This causes friction between the retraction device 15 and the Support surface 31b avoided under normal loads of the axial piston machine, whereby Frictional wear is reduced or, if load peaks do not occur, be avoided.
  • the hole space located radially outside of the stop pin 31 forms in functional operation the axial piston machine 1 has a secondary pressure chamber 42 which is passed through a channel 43, 44 is connected to a primary pressure chamber in which the Axial piston machine 1, a pressure prevails, which through the channel 43, 44 in the Pressure chamber 42 propagates and a radial at the outer end of the stop pin 31 generates inward thrust that overcomes the force of the spring 40 and the Stop pin 31 moves into its working position.
  • the primary pressure chamber it can e.g. B. act on the housing interior 3, in a sufficient leakage pressure during the functional operation of the axial piston machine 1 sets, which is able to generate the aforementioned thrust. It is too take into account that this interior pressure on the end face of the pin end 34 a Opposing force generated and therefore the effective differential area between the outer and the inner end face of the stop pin 31 or the interior pressure correspondingly large is to be measured.
  • a channel connection between the secondary pressure chamber 42 and the housing interior 3, which by a in the Housing wall 2a extending channel or through a lengthwise through the stop pin 31st extending bore 43a may be formed.
  • the Pressure chamber 42 through a running in the housing wall 2a, z. B.
  • both channels 43, 44 are sufficient for safe functional operation.
  • both channels 43, 44 can be present at the same time, only one or both channels can be connected to the associated pressure source.
  • a check valve 45, 46 is to be arranged in both channels 43, 44, its valve body 47, 48 in the direction of the associated pressure source closes.
  • the valve bodies 47, 48 can be biased into their closed position by a spring or they can be without Spring can be arranged freely movable.
  • the check valves 45, 46 limit a closed pressure chamber system in which the Pressure must be released before z. B. for disassembly of the inclined slide 11 or the retraction device 15, the stop pin 31 is displaceable into its release position. This can e.g. B. by at least slightly opening the sealing plug 39th respectively.
  • Another measure for automatic relaxation or delayed Relaxation of the pressure chamber system consists of the pressure chamber system by one connect small or restricted duct to the return system or the tank, the throttle is dimensioned as small as possible in order to avoid loss of power should be.
  • Such a relaxation channel 53 with a throttle 54 can, for. B. in Sealing plug 39 may be arranged, as indicated in the drawing.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Claims (12)

  1. Machine à pistons axiaux (1) comportant un boítier (2), un tambour de cylindre (5) agencé rotatif dans un espace intérieur (3) de boítier, dans lequel sont réalisés plusieurs perçages de cylindre (6) dans lesquels des pistons (7) sont guidés en déplacement, qui prennent appui via des patins de guidage (8) sur un plateau oscillant (11), un système de retour (15) sur lequel les patins de guidage (8) prennent appui lors du mouvement de retour du piston (7), et un système de retenue (16) monté dans le boítier (2) et déplaçable à l'encontre d'un ressort (40) pour soutenir le système de retour (15) sur le boítier (2), caractérisée en ce que le système de retenue (16) est sollicité par une chambre de pression (42) adjacente de telle sorte que le système de retenue (16) est poussé jusque dans l'espace intérieur (3) du boítier lorsqu'une pression est établie dans la chambre de pression (42), la chambre de pression (42) étant reliée avec l'espace intérieur (3) du boítier et/ou avec une conduite (44) amenant de la pression à l'état de fonctionnement pour la machine à pistons axiaux, et en ce que le système de retenue (16) est sollicité par le ressort (40) de telle sorte qu'il rétracte le système de retenue (16) hors de l'espace intérieur (3) du boítier lorsque la chambre de pression (42) est sensiblement exempte de pression.
  2. Machine à pistons axiaux selon la revendication 1, caractérisée en ce que le système de retenue (16) est agencé sur le côté sur lequel les pistons (7) effectuent chacun une course d'admission ou en ce qu'un système de retenue (16) est agencé sur les deux côtés.
  3. Machine à pistons axiaux selon l'une ou l'autre des revendications 1 et 2, caractérisée en ce que le système de retenue (16) est formé par un ou plusieurs tenons de butée (31) agencés les uns à côté des autres en direction périphérique du boítier (2) et qui sont chacun déplaçables dans un trou de guidage (32) approximativement radial dans le boítier (2) entre une position de travail poussée dans l'espace intérieur (3) du boítier, dans laquelle le tenon de butée (31) engage le système de retenue (15) par l'arrière sur sa face détournée du plateau oscillant (11), et une position de dégagement rétractée hors de l'espace intérieur (3) du boítier.
  4. Machine à pistons axiaux selon l'une des revendications précédentes, caractérisée en ce que la chambre de pression (42) est reliée à l'espace intérieur (3) du boítier par un premier canal de liaison (43) s'étendant dans la paroi de boítier (2a) associée ou en long à l'intérieur du tenon de butée (31).
  5. Machine à pistons axiaux selon l'une des revendications précédentes, caractérisée en ce que la conduite amenant la pression présente un deuxième canal de liaison (44) dans la paroi de boítier (2a), qui débouche dans la chambre de pression (42).
  6. Machine à pistons axiaux selon les revendications 4 et 5, caractérisée en ce que le premier canal de liaison (43) et le deuxième canal de liaison (44) sont présents en même temps et en ce qu'une soupape antiretour (45, 46) est agencée dans chacun de ces canaux de liaison (43, 44).
  7. Machine à pistons axiaux selon la revendication 6, caractérisée en ce que le système de chambre de pression limité par les soupapes antiretour (45, 46) et contenant la chambre de pression (42) est relié par une conduite étranglée (53) avec une conduite à une pression d'autant plus faible.
  8. Machine à pistons axiaux selon l'une des revendications 3 à 7, caractérisée en ce que le plateau oscillant (11) est monté pivotant autour d'un axe transversal, et un tenon de butée (31) est agencé dans un plan axial contenant l'axe de pivotement (14), de la machine à pistons axiaux (1), sur un ou sur les deux côtés de la machine à pistons axiaux (1), par rapport à l'axe rotatif (13) de la machine à pistons axiaux (1).
  9. Machine à pistons axiaux selon l'une des revendications précédentes, caractérisée en ce que la région de surface du système de retenue, qui est opposée au système de retour (15) dans là position de travail, s'étend radialement par rapport à l'axe de rotation (13) de la machine à pistons axiaux (1).
  10. Machine à pistons axiaux selon l'une des revendications 7 à 9, caractérisée en ce que le tenon de butée (31) est arrondi en forme convexe sur sa face tournée vers le système de retour (15) et présente de préférence une section transversale de forme cylindrique.
  11. Machine à pistons axiaux selon l'une des revendications précédentes, caractérisée en ce qu'entre le plateau oscillant (11) et le système de retenue (16) est prévu un espacement (a) axial qui est seulement dimensionné de telle sorte qu'au fonctionnement de la machine à pistons axiaux (1), le système de retour (15) bute contre le système de retenue (16) avant que le système de retour (15) soit déformé au-delà de sa limite de déformation élastique.
  12. Machine à pistons axiaux selon l'une des revendications 3 à 11, caractérisée en ce que le trou de guidage (32) est un trou à gradins et le tenon de butée (31) est une goupille à gradins, une surface de gradin (37, 38) limitant le mouvement du tenon de butée (31) jusque dans sa position de travail.
EP98121508A 1997-12-03 1998-11-13 Machine à pistons axiaux Expired - Lifetime EP0921312B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19753654A DE19753654C2 (de) 1997-12-03 1997-12-03 Axialkolbenmaschine
DE19753654 1997-12-03

Publications (3)

Publication Number Publication Date
EP0921312A2 EP0921312A2 (fr) 1999-06-09
EP0921312A3 EP0921312A3 (fr) 2000-04-05
EP0921312B1 true EP0921312B1 (fr) 2003-08-06

Family

ID=7850629

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98121508A Expired - Lifetime EP0921312B1 (fr) 1997-12-03 1998-11-13 Machine à pistons axiaux

Country Status (2)

Country Link
EP (1) EP0921312B1 (fr)
DE (2) DE19753654C2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19909311C2 (de) * 1999-03-03 2001-01-25 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine
DE10035630C1 (de) 2000-07-21 2002-03-14 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit einer Rückzugeinrichtung
DE102004043745B3 (de) * 2004-09-10 2006-02-09 Danfoss A/S Hydraulische Axialkolbenmaschine

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3453965A (en) * 1966-08-29 1969-07-08 Applied Power Ind Inc Valve plate motor pump
US3631763A (en) * 1970-01-02 1972-01-04 Sperry Rand Corp Power transmission
US3587403A (en) * 1970-01-16 1971-06-28 Sperry Rand Corp Power transmission
US3605565A (en) * 1970-03-13 1971-09-20 Sperry Rand Corp Power transmission
US4111103A (en) * 1977-02-14 1978-09-05 Commercial Shearing, Inc. Thrust rings for swash plate pumps and motors

Also Published As

Publication number Publication date
DE59809197D1 (de) 2003-09-11
EP0921312A3 (fr) 2000-04-05
EP0921312A2 (fr) 1999-06-09
DE19753654A1 (de) 1999-06-17
DE19753654C2 (de) 1999-10-21

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