EP0697520A1 - Rotule d'appui d'un piston d'une machine hydraulique radiale ou axiale - Google Patents

Rotule d'appui d'un piston d'une machine hydraulique radiale ou axiale Download PDF

Info

Publication number
EP0697520A1
EP0697520A1 EP95112878A EP95112878A EP0697520A1 EP 0697520 A1 EP0697520 A1 EP 0697520A1 EP 95112878 A EP95112878 A EP 95112878A EP 95112878 A EP95112878 A EP 95112878A EP 0697520 A1 EP0697520 A1 EP 0697520A1
Authority
EP
European Patent Office
Prior art keywords
piston
ball head
bearing surface
ball
plane
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
EP95112878A
Other languages
German (de)
English (en)
Other versions
EP0697520B1 (fr
Inventor
Ludwig Wagenseil
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 EP0697520A1 publication Critical patent/EP0697520A1/fr
Application granted granted Critical
Publication of EP0697520B1 publication Critical patent/EP0697520B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0082—Details
    • F01B3/0085—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
    • F04B1/12—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
    • 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
    • F04B1/20—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 rotary cylinder block
    • F04B1/2014—Details or component parts

Definitions

  • the invention relates to a ball head according to the preamble of claim 1.
  • Ball heads of this type are known for example from DE-PS 4 024 319, which describes a swash plate pump, the pistons of which are supported on the swash plate indirectly via piston rods.
  • Each piston rod has at its opposite ends a spherical head, which in a hollow spherical section in the piston or in the lifting body, i.e. in the swashplate.
  • ball heads of the type mentioned at the outset are known from DE-OS 2 307 641, which describes a radial piston machine, the pistons of which are supported indirectly via sliding shoes on the lifting body designed in the form of an outer ring.
  • the ball heads are formed on the slide shoes and are received in corresponding hollow ball sections in the piston.
  • the known ball heads described above each have a larger diameter than the circular openings of the associated hollow ball sections, in which they are rotatably mounted and in which they can only be used with the aid of the cylinder surfaces, provided that the corresponding inclination of the respective piston rod or the slide shoe Plane of the cylinder surface is brought into a position parallel to the plane of the circular opening.
  • the ball heads are hydrostatically relieved in the hollow ball sections in a known manner.
  • a so-called pressure pocket in the form of a recess is formed in the spherical caps or in the bearing surfaces, to which pressure oil is supplied, which flows out through the bearing gap between the spherical cap and the bearing surface, forming a hydrostatic pressure field to the leakage oil chamber of the axial piston machine.
  • the swash plate 1 exerts a normal force F N on the ball head K, which acts in the center of gravity S of the pressure field or the spherical cap KK and in the ball head K into a piston force F K and a radial - or transverse force F R is broken down.
  • the radial force F R is proportional to the distance x between said surface center of gravity S and the piston axis L K and can move the ball head K in the hollow spherical section KA to the left in FIG.
  • the swivel angle of the axial or radial piston machine has no influence on the magnitude of the radial force and thus the pressure field if the relief groove is formed in the spherical cap.
  • the relief groove preferably runs in a plane perpendicular to the piston axis.
  • Other options for the course of the relief groove are also conceivable, for example in a plane perpendicular to the plane mentioned or to the plane of the equator line.
  • the axial piston machine shown in FIG. 1 is designed in an inclined-axis design with an adjustable displacement volume and, in a known manner, comprises, as known components, a hollow cylindrical housing 10 with an open end on the front side, a housing end plate 11 closing this open end, a drive shaft 12 with a drive disk 13 formed in one piece , a control body 14 with an associated adjusting device 15 and a cylinder drum 16.
  • the drive shaft 12 passes through a through hole formed in the housing end wall 17 opposite the housing end plate 11 and is rotatably mounted in the latter.
  • the drive pulley 13 is in the interior of the housing arranged and rotatably supported on its inner surface on the inner surface of the housing end wall 17.
  • the control body 14 is a so-called control lens of biconvex shape, which can be displaced in a circular support and pivot bearing 18 in the housing end plate 11 and can be fixed within this bearing by means of the adjusting device 15 in any desired position.
  • two opposing control kidneys, not shown, are formed in a known manner, which are connected to the pressure port and the suction port (also not shown) of the inclined axis machine.
  • the adjusting device 15 is provided for changing the displacement volume of the inclined axis machine and comprises a pin 19 and an actuating rod 20 which is guided in a bore 21 perpendicular to the drive shaft 12 in the housing end plate 11.
  • the pin 19 is fastened to the actuating rod 20 and engages in a bore 22 in the control body 14.
  • the cylinder drum 16 is arranged between the drive pulley 13 and the control body 14 and is supported for the purpose of self-centering mounting with a concave bearing surface on the convex control surface of the control body 14 facing it.
  • cylindrical bores 23 are formed, which open out via outlet channels 24 on the concave bearing surface of the cylinder drum 16 and connect the cylinder bores 23 via the control kidneys with the pressure and suction nozzle when the latter rotates .
  • pistons 25 are arranged so that they can be moved back and forth. Their free ends are rotatably connected to the drive pulley 13 via ball joints.
  • Each ball joint consists of a ball head K formed at the free end of the associated piston 25 and a hollow ball section KA formed in the drive disk 13 (see FIG. 2), in which the ball head K is accommodated in a rotatable manner.
  • the hollow spherical sections KA are arranged on a pitch circle that is slightly smaller or larger than the pitch circle of the Cylinder rooms 23 is.
  • a compression spring 26 which supports a central pin 27 on the cylinder drum 16, which is also supported by a ball and socket joint in the drive pulley 13, projects into the stepped bore and guides the cylinder drum 16, and thus supports it when no oil pressure forces occur , in contact with the control body 14.
  • each piston 25 essentially correspond to the pistons described in DE-AS 2 358 870 and are therefore not described in more detail here. It should only be mentioned that each piston 25 has a piston ring 28 received in a groove, to which a section in the form of a spherical zone connects in the direction of the piston head. The piston sections between this spherical zone and the piston crown and above the piston ring 28 are frustoconical.
  • Each hollow spherical section KA is delimited by a circular opening 29 which lies in a plane E 1 which is parallel to the end face 30 of the drive pulley 13 and is set back to this by a small amount.
  • a conical surface 31 connects the hollow spherical section KA at the level of the circular opening 29 with the end face 30 of the drive pulley 13.
  • the diameter of the circular opening 29 is smaller than that of the hollow spherical section KA and the spherical head K accommodated therein.
  • the spherical head K is formed with a cylindrical surface 32 which runs symmetrically on both sides of a spherical head equatorial line Q which, with the piston axis L K, includes an angle ⁇ deviating from 90 ° and one has a smaller diameter than the circular opening 29.
  • the assembly and disassembly of the ball head K can only take place if the piston 25 is brought into such an inclined position that the cylinder surface 32 or the equator line Q is parallel to the plane E 1 of the circular opening 29.
  • the piston 25 is pivoted clockwise by the angle ⁇ into the inclined position shown in FIG it is no longer possible to remove the spherical head K from the hollow spherical section KA.
  • This inclination corresponds to a swivel angle of 0 ° enclosed by the drive shaft axis L T and the cylinder drum axis L Z of the axial piston machine and thus a zero displacement volume.
  • the axial piston machine is set to the maximum pivoting angle shown in FIG. 3, that is to say to the maximum displacement volume.
  • the cylinder surfaces 32 on the respective spherical head K each have a spherical cap KK, in which a relief groove 33 extends in a plane E 2 perpendicular to the piston axis L K and has two open ends which it opens into the cylindrical surface 32 or in the cavity 34 defined by this and the concave surface of the hollow spherical section KA.
  • the bearing gap h is not shown in FIG. 2.
  • the area of the concave surface of the hollow spherical section KA corresponding to the swivel angle range of the axial piston machine represents a bearing surface 35 on which the ball head K is supported with the bearing counter surface 36 delimited by the relief groove 33 on the spherical cap KK under hydrostatic relief by a pressure field.
  • each piston 25 is provided with a through bore 37, which is only shown in FIGS supplies the working space 39 of the cylinder bore 23.
  • a portion of this pressure oil flows through through holes 40 in the drive pulley 13 to pressure pockets 41 in the drive pulley ring surface.
  • a pressure field is also built up, which rotatably supports the drive pulley 13 on the housing end wall 17.
  • hydrostatic relief in the sense of the invention also includes the so-called “hydrostatic bearing", in which the so-called inlet pressure in the pressure pocket 38 due to the use of a throttle in the through bore 37 is lower than the so-called supply pressure with which the pressure oil flows from the working space 39.
  • hydrostatic bearing in which the so-called inlet pressure in the pressure pocket 38 due to the use of a throttle in the through bore 37 is lower than the so-called supply pressure with which the pressure oil flows from the working space 39.
  • both pressures are essentially the same.
  • the function of the relief groove is described below using the example of the hydrostatic bearing.
  • the pressure oil supplied to the pressure pocket 38 via the through-bore 37 with a throttle flows with the inlet pressure via the bearing gap h between the bearing counter surface 36 and the corresponding area of the bearing surface 35 directly on the one hand and on the other hand via the relief groove 33 into the cavity 34 between the cylinder surface 32 and the concave surface of the hollow ball section KA and from there to the leakage oil chamber.
  • the oil film in the gap h forms a pressure field which absorbs the piston force F K and thus prevents metallic contact between the ball head K and the concave surface of the hollow ball section KA.
  • the center of gravity S of the pressure field or the bearing counter surface 36 and thus the point of application of the piston force F N on the ball head K is at a smaller distance x than in the prior art (cf. FIG. 5) from the piston axis L. K , in the region of the point of penetration of the piston axis L K through the bearing counter surface 36.
  • the circular line with the radius x shows the position of the center of gravity S with the piston 25 rotating about its piston axis L K.
  • the radial force F R is smaller compared to the prior art corresponding to the smaller distance x, namely by such a value that no displacement of the ball head K can take place.
  • the end face 30 of the drive pulley 13 is selected in the form of a conical surface with an inclination angle ⁇ with respect to a plane E 3 perpendicular to the drive shaft axis L T. Passes through the apex of this conical surface 30 the drive shaft axis L T.
  • the angle ⁇ corresponds to the deflection angle of the pistons, which arises due to the formation of ellipses during the rotation of the drive shaft with the cylinder drum running at an angle.
  • This arrangement ensures optimal utilization of the retraction function of the hollow spherical sections as a result of their bearing surfaces enclosing the spherical heads at an angle greater than 180 °, since the piston offset during the revolution is almost symmetrical at the maximum swivel angle.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP95112878A 1994-08-16 1995-08-16 Rotule d'appui d'un piston d'une machine hydraulique radiale ou axiale Expired - Lifetime EP0697520B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4429053 1994-08-16
DE4429053A DE4429053C1 (de) 1994-08-16 1994-08-16 Kugelkopf zur Abstützung eines Kolbens einer hydrostatischen Axial- oder Radialkolbenmaschine an deren Hubkörper

Publications (2)

Publication Number Publication Date
EP0697520A1 true EP0697520A1 (fr) 1996-02-21
EP0697520B1 EP0697520B1 (fr) 1997-10-08

Family

ID=6525833

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95112878A Expired - Lifetime EP0697520B1 (fr) 1994-08-16 1995-08-16 Rotule d'appui d'un piston d'une machine hydraulique radiale ou axiale

Country Status (2)

Country Link
EP (1) EP0697520B1 (fr)
DE (2) DE4429053C1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104074738A (zh) * 2014-06-30 2014-10-01 徐州徐工液压件有限公司 一种柱塞泵、柱塞马达及其免收口正包柱塞滑靴组件
US9850757B2 (en) 2014-04-08 2017-12-26 Linde Hydraulics Gmbh & Co. Kg Axial piston machine utilizing a bent-axis construction
IT201900001613A1 (it) * 2019-02-05 2020-08-05 Dana Motion Sys Italia Srl Pistone per macchine idrauliche a pistoni assiali.

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006019884B4 (de) * 2006-04-28 2008-04-17 Sauer-Danfoss Gmbh & Co Ohg Hydrostatische Axialkolbenmaschine in Schrägachsenbauweise
DE102009058332B4 (de) * 2009-12-15 2019-11-28 Robert Bosch Gmbh Axialkolbenmaschine
US9212656B2 (en) 2011-02-21 2015-12-15 Honeywell International Inc. Piston-to-shoe interface lubrication method
DE102012222172A1 (de) * 2012-12-04 2014-06-05 Robert Bosch Gmbh Axialkolbenmaschine mit kegelförmigem Kolben
US9664184B2 (en) * 2013-05-22 2017-05-30 Hydac Drive Center Gmbh Axial piston pump having a swash-plate type construction
DE102016100920A1 (de) 2015-11-11 2017-05-11 Linde Hydraulics Gmbh & Co. Kg Hydrostatische Axialkolbenmaschine in Schrägachsenbauweise
EP3168469B1 (fr) 2015-11-11 2019-06-05 Linde Hydraulics GmbH & Co. KG Hydrostatische axialkolbenmaschine in schrägachsenbauweise
DE102018218547A1 (de) 2018-10-30 2020-04-30 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2638850A (en) * 1952-01-24 1953-05-19 Ferris Walter Piston assembly for axial type hydrodynamic machines
DE2307641A1 (de) 1973-02-16 1974-08-22 Bosch Gmbh Robert Kugelgelenk
DE2358870A1 (de) * 1973-11-26 1975-05-28 Hydromatik Gmbh Axialkolbenmaschine mit einstueckigem kolben
DE4024319A1 (de) 1989-07-31 1991-02-07 Honda Motor Co Ltd Hydraulische taumelscheibeneinrichtung
DE4214765A1 (de) * 1992-05-04 1993-11-11 Sachsenhydraulik Gmbh Kolben-Gleitschuh Verbindung für hydro-statische Maschinen

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2638850A (en) * 1952-01-24 1953-05-19 Ferris Walter Piston assembly for axial type hydrodynamic machines
DE2307641A1 (de) 1973-02-16 1974-08-22 Bosch Gmbh Robert Kugelgelenk
DE2358870A1 (de) * 1973-11-26 1975-05-28 Hydromatik Gmbh Axialkolbenmaschine mit einstueckigem kolben
DE4024319A1 (de) 1989-07-31 1991-02-07 Honda Motor Co Ltd Hydraulische taumelscheibeneinrichtung
DE4214765A1 (de) * 1992-05-04 1993-11-11 Sachsenhydraulik Gmbh Kolben-Gleitschuh Verbindung für hydro-statische Maschinen

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9850757B2 (en) 2014-04-08 2017-12-26 Linde Hydraulics Gmbh & Co. Kg Axial piston machine utilizing a bent-axis construction
CN104074738A (zh) * 2014-06-30 2014-10-01 徐州徐工液压件有限公司 一种柱塞泵、柱塞马达及其免收口正包柱塞滑靴组件
IT201900001613A1 (it) * 2019-02-05 2020-08-05 Dana Motion Sys Italia Srl Pistone per macchine idrauliche a pistoni assiali.

Also Published As

Publication number Publication date
EP0697520B1 (fr) 1997-10-08
DE4429053C1 (de) 1995-11-02
DE59500767D1 (de) 1997-11-13

Similar Documents

Publication Publication Date Title
EP0044070B1 (fr) Pompe à pistons axiaux avec deux courants d'écoulement
EP0941403B1 (fr) Moteur a pistons axiaux a rin age des paliers
DE3942189C1 (fr)
EP0697520B1 (fr) Rotule d'appui d'un piston d'une machine hydraulique radiale ou axiale
DE2448594C3 (de) Axialkolbenmaschine
DE3780496T2 (de) Schwenkkoerperschmierung fuer axialkolbenmaschine.
DE19645580C1 (de) Axialkolbenmaschine mit Dämpfungselement für die Schräg- oder Taumelscheibe
DE3519783A1 (de) Axialkolbenmaschine
EP0728945B1 (fr) Machine à pistons axiaux
DE2029087C3 (de) Hydrostatisches Längs-Gleitlager für den Triebflansch einer Druckflüsslgkeits-Schwenktrommel-Axialkolbenmaschine
DE19712348A1 (de) Taumelscheibenkompressor mit einfach-wirkenden Kolben
CH691272A5 (de) Hubkolbenmaschine mit Taumelscheibengetriebe.
EP0675286B1 (fr) Machine à pistons axiaux avec décharge hydrostatique du palier du plateau d'impulseur
DE19527649B4 (de) Axialkolbenmaschine
DE2641158A1 (de) Axialkolbenpumpe
EP1700034B1 (fr) Machine a pistons axiaux pour realiser un acheminement independant dans plusieurs circuits hydrauliques
EP0465796B1 (fr) Machine à piston du type à axe incliné
EP0763657B1 (fr) Machine à pistons axiaux ayant des patins glissants à contrainte réduite
DE102020211284A1 (de) Hydrostatische Axialkolbenmaschine in Schrägscheibenbauweise
EP1041279B1 (fr) Plaque de valves pour une machine axiale à piston
DE69019152T2 (de) Lagerschmierung in axialkolbenfluideinrichtungen.
DE19643389C1 (de) Axialkolbenmaschine mit variabler Fixierung der Steuerscheibe
DE2248312C3 (de) Hydrostatische Radialkolbenmaschine
DE1653418B2 (de) Schrägscheibenlagerung für Axialkolbenmaschinen
DE4030545C2 (de) Verstellbare Axialkolbenmaschine in Schrägscheibenbauweise

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT SE

17P Request for examination filed

Effective date: 19960315

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

17Q First examination report despatched

Effective date: 19970121

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

ITF It: translation for a ep patent filed

Owner name: JACOBACCI & PERANI S.P.A.

ET Fr: translation filed
REF Corresponds to:

Ref document number: 59500767

Country of ref document: DE

Date of ref document: 19971113

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19980108

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20070822

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20070823

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20070815

Year of fee payment: 13

Ref country code: IT

Payment date: 20070827

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20070812

Year of fee payment: 13

EUG Se: european patent has lapsed
GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20080816

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20090430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080816

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080901

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090303

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080816

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080817