EP0300274B1 - Machine à pistons axiaux différentiels - Google Patents

Machine à pistons axiaux différentiels Download PDF

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Publication number
EP0300274B1
EP0300274B1 EP88110805A EP88110805A EP0300274B1 EP 0300274 B1 EP0300274 B1 EP 0300274B1 EP 88110805 A EP88110805 A EP 88110805A EP 88110805 A EP88110805 A EP 88110805A EP 0300274 B1 EP0300274 B1 EP 0300274B1
Authority
EP
European Patent Office
Prior art keywords
machine according
axial piston
piston machine
piston
passage
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
EP88110805A
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German (de)
English (en)
Other versions
EP0300274A1 (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.)
Hydromatik GmbH
Original Assignee
Hydromatik GmbH
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Filing date
Publication date
Application filed by Hydromatik GmbH filed Critical Hydromatik GmbH
Publication of EP0300274A1 publication Critical patent/EP0300274A1/fr
Application granted granted Critical
Publication of EP0300274B1 publication Critical patent/EP0300274B1/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
    • F04B5/00—Machines or pumps with differential-surface 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

Definitions

  • the invention relates to an axial piston machine according to the preamble of claim 1.
  • the cylinder rooms can be connected to two separate flow lines to e.g. to achieve a throughput distribution, cf. US Pat. No. 3,126,835, or one of the two cylinder spaces, can also only be used to press the piston or pistons against an existing drive inclined surface or an optionally existing cylinder drum against the control mirror, cf. DE-PS 707 462.
  • the cylinder spaces can also be switched as described in US Pat. No. 2,737,899, the larger cylinder space serving as a pre-compression chamber for the smaller cylinder space in order to achieve keise-high pressures without cavitation.
  • the invention has for its object to design an axial piston machine with step piston of the type mentioned in such a way that the relief of the plain bearing depending on the respective operating state of the axial piston machine.
  • the invention is based on the knowledge that, in the known embodiment, a hydrostatic mounting of the pistons on the drive surface due to the fluid cushion as a function of the respective load, i.e. of the axial force with which the piston is pressed against the drive surface is not possible because the pressure force component, which is dependent on the pressure in the second cylinder chamber, is not taken into account.
  • both the pressure in the first cylinder chamber and that in the second cylinder chamber can change for various reasons, e.g. in an axial piston machine with two throughput circuits due to different power consumption of the connected consumers.
  • the drive-side slide bearing of the piston is provided with a second hydrostatic bearing which is independent of the first hydrostatic bearing and which is connected to the second cylinder chamber by a channel and which is therefore effective as a function of the pressure in the second cylinder chamber.
  • the piston forces actually present are thus taken into account to relieve the sliding bearing, which leads to a more balanced hydrostatic bearing of the piston.
  • pressure pockets for three- or multi-stage pistons to be provided in the appropriate number, ie a pressure pocket with a separate connecting channel leading to the associated pressure chamber is to be arranged for each cylinder chamber of the piston.
  • hydrostatic bearings according to the invention on the flat sliding surfaces between a swash plate and a sliding shoe receiving the piston head and / or between the surface of a spherical piston head and the spherical inner surface of a bearing shell or spherical cap receiving the latter.
  • the essential individual parts of the axial piston machine are a housing 4 consisting of a cup-shaped housing part 2 and a housing cover 3, and the cup-shaped housing part 2 or the cavity 5 of the housing 4 passing through the central axis 6 and in the radial wall 7 of the housing part 2 and in the housing cover 3, the drive shaft 8, a cylinder 9 with a plurality of diametrically opposed or star-shaped arranged essentially axially extending piston bores 11, in which correspondingly sized pistons 12 are slidably mounted, which can be driven by an axially displaceable sliding surface 13.
  • the cylinder 9 is formed by a cylinder drum, which is arranged on the drive shaft 8 by means of a central hole and is non-rotatably connected to it by a toothed coupling 14, and, with its end face 15 facing away from the sliding surface 13, bears against a control mirror 16 which bears against a control plate 17 is formed, which is fastened by screws or centering pins to the housing cover 4, in which two supply and discharge lines 18, 19, 21, 22 for the fluid, in the present case oil, are formed.
  • the control plate 17 there are two pairs of opposing, kidney-shaped control channels 23, 24, which correspond to axial flow channels 25, 26, which are connected to the piston bores 11 and the supply and discharge lines 18, 19, 21, 22.
  • the piston bores 11 and piston 12 are step bores and correspondingly dimensioned step pistons, as a result of which first cylinder spaces 27, which are delimited by the end face 28 of the pistons 12, and second cylinder spaces 29, which are delimited by the step surfaces 30 of the pistons 12, are formed are, in each case in the first cylinder space 27, the throughput channel 25 and in the second cylinder space 29, the second throughput channel 26 arranged radially inward from the first throughput channel 25.
  • the pistons 12 have spherical piston heads 32 at their drive-side ends, which are pivotally supported on all sides in the piston heads 32 above and behind-reaching calottes 33 of slide shoes 34.
  • the sliding shoes 34 lie with flat sliding surfaces 35 on the flat inclined surface 36 of a swash plate 37, which is fitted on its drive side with a sliding ring 38 made of wear-resistant material, and whose angle w, which it encloses with a radial transverse plane of the axial piston machine, for the purpose of changing the Throughput volume of the axial piston machine 1 can be changed arbitrarily.
  • the sliding shoes 34 On their side facing the cylinder 9, the sliding shoes 34 have shoulders 39 and, with a projection 41 containing the spherical caps 33, they pass through a retraction plate 42 in holes 43, the shoulders 39 abutting the retraction plate 42, both axially by means of a spherical support head can also be supported radially, which can be acted upon axially against the inclined surface 36 by means of a compression spring (not shown).
  • hydrostatic bearings are formed, in which fluid or oil cushions in communication with the cylinder spaces 27, 29 are connected by recesses through channels 52, 53 formed first and second pressure pockets 54, 55 are effective, which act on the associated piston 12 as a function of the existing pressure in the cylinder spaces 27, 29 against the piston force shown as arrow 58, in order to significantly reduce the latter and thus in the Bearings 49, 51 to reduce the resulting friction.
  • third and fourth pressure pockets 56, 57 in at least one of the spherical sliding surfaces 46, 47, which form hydrostatic bearings for the piston joint 48 due to a corresponding connection with the cylinder spaces 27, 29.
  • the first channel 52 originating from the first cylinder space 27 and the associated first and third pressure pockets 54, 56 and the second channel 53 originating from the second cylinder space 29 as well as the associated second and fourth pressure pockets 55, 57 form separate pressure systems which pass through the sliding surfaces 35, 36, 46, 47 are separated from each other. As a result, the pressure in the associated cylinder space 27 or 29 can only affect the associated hydrostatic pads.
  • a sleeve 61 is inserted axially into each central piston 12 in a central longitudinal bore 62 and fastened to it, for example by pressing, gluing, pinning or screwing, the sleeve 61 having an axial passage through which the swash plate 37 faces away from it Throttle 63 arranged at the end and a channel section 69 (bore) enlarged in cross section compared to the latter.
  • Throttle 63 arranged at the end and a channel section 69 (bore) enlarged in cross section compared to the latter.
  • the sleeve 61 automatically forms the third pressure pocket 56 due to the lack of a spherical shape of its end face.
  • the first channel 52 consists of a section of the longitudinal bore 62, the throttle 63, the channel section 69, the first and the third pressure pockets 54, 56 and a channel section 65 connecting the latter to one another in the sliding block 34.
  • the second channel 53 consists of a radial channel section 66 in the piston 12 in the vicinity of its stepped surface 30, a circumferential groove 67 or taper on the sleeve 61, a channel section 68 and, in the present case, extending radially from the circumferential groove 67 to the fourth pressure pocket 57 in the form of a spherical zone a channel section 70 connecting the pressure pockets 55, 57 to one another, in the present case oblique.
  • the third and fourth pressure pockets 56 and 57 are located in the spherical surface 47 of the piston head 32 and the first and second pressure pockets 54 and 55 are located in the sliding surface 35 of the sliding block 34.
  • the circumferential groove 67 or the distance between the channel sections 66 and 68 is dimensioned smaller than the length 1 of the sleeve 61, so that the latter has sections at its ends with which it is fully and firmly received in the longitudinal bore 62.
  • the first pressure pocket 54 has a circular shape and the second pressure pocket 55 has a circular ring shape, wherein they are arranged concentrically to one another.
  • an annular groove 71 is arranged between them, each at a distance from them, which is connected to the cavity 5 of the housing 4 by a channel 72 extending through the sliding block 34, ie is vented.

Landscapes

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

Claims (12)

1. Machine à pistons axiaux (1) dont les pistons (12) sont sous la forme de pistons différentiels et délimitent une première chambre du cylindre (27) ainsi qu'au moins une deuxième chambre du cylindre (29), les pistons (12) étant entraînés, sur le côté d'entraînement, par une surface d'entraînement (13) pouvant être déplacée axialement, sur laquelle ils glissent dans un palier de glissement à poches de pression (54, 56) qui sont reliées par un canal (52, 63, 65) à la première chambre du cylindre (27), caractérisée en ce que la deuxième chambre du cylindre (29) est reliée par un deuxième canal (53) distinct du premier canal (52) à une deuxième poche de pression (55, 57) sur une des deux surfaces de glissement (35, 36, 46,47) du palier de glissement.
2. Machine à pistons axiaux selon la revendication 1, caractérisée en ce que la première et la deuxième poches de pression (54, 55) sont ménagées dans la surface de glissement (35) d'un patin de glissement (34).
3. Machine à pistons axiaux selon la revendication 1 ou 2, caractérisée en ce que le premier et le deuxième canaux (52, 53) s'étendent au moins sur une section longitudinale du piston (12) en traversant le piston (12) dans sa longueur.
4. Machine à pistons axiaux selon la revendication 3, caractérisée en ce que les canaux (52, 53) s'étendent coaxialement l'un à l'autre.
5. Machine à pistons axiaux selon la revendication 3 ou 4, caractérisée en ce que le premier canal et/ou le deuxième canal (52, 53) s'étend dans une douille (61) insérée dans le piston (12) ou bien est délimité par celle-ci.
6. Machine à pistons axiaux selon la revendication 5, caractérisée en ce que le deuxième canal (53) est constitué, dans la région de la section longitudinale du piston (12), par un évidement (67) tel qu'une rainure, en particulier par une gorge annulaire sur la surface périphérique de la douille (61).
7. Machine à pistons axiaux selon la revendication 5 ou 6, caractérisée en ce que l'évidement (67) sur la surface périphérique de la douille (61) est relié, par un canal transversal (66) qui s'étend de préférence au voisinage de la surface en gradin (30) et/ou par un canal transversal (68) qui s'étend dans la région de la tête de piston (32), à la deuxième chambre (29) du cylindre, et/ou à la deuxième poche de pression (55).
8. Machine à pistons axiaux selon la revendication 7, caractérisée en ce que le canal transversal (66 et/ou 68) est conformé sous la forme d'un étranglement, ou en ce qu'un étranglement est inséré dans le canal transversal (66 et/ou 68).
9. Machine à pistons axiaux selon l'une des revendications 1 à 8, caractérisée en ce que le piston (12) présente une tête de piston (32) de forme sphérique qui se loge de manière pivotante dans une calotte (33) d'un plateau oblique (37) ou d'un patin de glissement (34) prenant un appui glissant contre ce plateau, et en ce que la première et la deuxième poches de pression (56, 57) sont disposées dans au moins une des deux surfaces de glissement sphériques (35, 36) de l'articulation (48) du piston, de préférence dans la surface sphérique de glissement (47) de la tête du piston (32).
10. Machine à pistons axiaux selon une des revendications 1 à 9, caractérisée en ce que la deuxième ou la quatrième poche à pression (55, 57) est disposée concentriquement à la première ou à la troisième poche à pression (54, 56), de préférence en entourant cette dernière de manière annulaire.
11. Machine à pistons axiaux selon la revendication 10, caractérisée en ce qu'entre la première et la deuxième poche à pression (54, 55, 56, 57) est prévu un évidement (71), de préférence de forme annulaire, dans une des surfaces de glissement, de préférence dans celle du patin (34), cet évidement étant relié par un canal (72) avec la cavité (5) du boîtier.
12. Machine à pistons axiaux selon une des revendications 3 à 11, caractérisée en ce qu'un étranglement (63) est ménagé dans la douille (61) ou inséré dans celle-ci, de préférence dans l'extrémité de la douille (61) éloignée du plateau oblique (37).
EP88110805A 1987-07-20 1988-07-06 Machine à pistons axiaux différentiels Expired - Lifetime EP0300274B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873723988 DE3723988A1 (de) 1987-07-20 1987-07-20 Axialkolbenmaschine, deren kolben als stufenkolben ausgebildet sind
DE3723988 1987-07-20

Publications (2)

Publication Number Publication Date
EP0300274A1 EP0300274A1 (fr) 1989-01-25
EP0300274B1 true EP0300274B1 (fr) 1991-03-20

Family

ID=6331968

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88110805A Expired - Lifetime EP0300274B1 (fr) 1987-07-20 1988-07-06 Machine à pistons axiaux différentiels

Country Status (4)

Country Link
US (1) US4852463A (fr)
EP (1) EP0300274B1 (fr)
JP (1) JP2527993B2 (fr)
DE (2) DE3723988A1 (fr)

Families Citing this family (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19522827B4 (de) * 1995-06-23 2005-12-22 Danfoss A/S Hydraulische Axialkolbenmaschine
US6557455B2 (en) * 2000-10-02 2003-05-06 Caterpillar Inc. Two piece barrel design for a hydraulic oil pump
EP1715183B1 (fr) * 2002-07-05 2008-08-06 Bieri Hydraulik Ag Pompe hydraulique à pistons axiaux
US20040042906A1 (en) * 2002-08-28 2004-03-04 Gleasman Vernon E. Long-piston hydraulic machines
US6983680B2 (en) * 2002-08-28 2006-01-10 Torvec, Inc. Long-piston hydraulic machines
US7416045B2 (en) * 2002-08-28 2008-08-26 Torvec, Inc. Dual hydraulic machine transmission
US6840879B1 (en) 2002-09-03 2005-01-11 Hydro-Gear Limited Partnership Hydraulic motor apparatus
US6811510B1 (en) * 2002-09-03 2004-11-02 Hydro-Gear Limited Partnership Hydraulic motor apparatus and vehicle
US6811509B1 (en) 2002-09-03 2004-11-02 Hydro-Gear Limited Partnership Hydraulic motor apparatus including brake mechanism
US7081061B1 (en) 2002-09-03 2006-07-25 Hydro-Gear Limited Partnership Hydraulic motor apparatus
DE10349599B3 (de) * 2003-10-24 2005-07-07 Brueninghaus Hydromatik Gmbh Anschlussblock für eine hydrostatische Kolbenmaschine
DE10356155B4 (de) * 2003-12-02 2006-06-14 Brueninghaus Hydromatik Gmbh Hydrostatisches Antriebssystem mit pumpenseitiger Hydraulikfluidmengenteilung
US7273355B2 (en) * 2003-12-15 2007-09-25 Tecumseh Products Company Compressor assembly with piston having multiple cross sections
US7175400B2 (en) * 2003-12-15 2007-02-13 Tecumseh Products Company Compressor assembly with reciprocating piston and vented cylinder
US7475617B2 (en) * 2005-06-15 2009-01-13 Torvec, Inc. Orbital transmission with geared overdrive
DE102006046128A1 (de) * 2006-06-02 2007-12-06 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit hydrostatischer Auflage des Niederhalters
DE102006035708A1 (de) * 2006-08-01 2008-02-07 Robert Bosch Gmbh Fahrzeugbremsanlagen-Kolbenpumpe mit einem Kolben
DE102012004302A1 (de) 2012-03-01 2013-09-05 Robert Bosch Gmbh Elektrohydraulisches System
JP6275502B2 (ja) * 2014-02-12 2018-02-07 川崎重工業株式会社 液圧回転装置のシューおよび液圧回転装置
JP2015178808A (ja) * 2014-03-19 2015-10-08 カヤバ工業株式会社 液圧回転機
CN103939329B (zh) * 2014-04-29 2016-08-24 同济大学 一种柱塞式液压泵用间隙补偿式环形油槽滑靴
US10273865B2 (en) * 2015-12-24 2019-04-30 Rabhi Vianney Cooling and lubricating system for a piston sealing device
JP6854160B2 (ja) * 2017-03-16 2021-04-07 日立建機株式会社 斜板式液圧回転機械
JP6854161B2 (ja) * 2017-03-16 2021-04-07 日立建機株式会社 斜板式液圧回転機械
US10634246B2 (en) * 2017-09-05 2020-04-28 Vianney Rabhi Hydraulic piston with cooling and lubrication valve
CN107905973B (zh) * 2017-10-30 2019-05-31 华中科技大学 一种多级压缩机

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Publication number Priority date Publication date Assignee Title
US3126835A (en) * 1964-03-31 Fluid pump
DE707462C (de) * 1938-12-02 1941-06-23 Rudolf Mueller Kolbenpumpe mit in einer Zylindertrommel im Kreise angeordneten parallelen Kolben
US2737899A (en) * 1951-06-30 1956-03-13 Denison Eng Co Axial piston pump
US3106138A (en) * 1960-06-27 1963-10-08 Hans Toma Piston type hydrostatic power units
US3142262A (en) * 1960-08-31 1964-07-28 Council Scient Ind Res Pressure fluid pistons or plungers
FR1487165A (fr) * 1966-07-21 1967-06-30 Hydromatik G M B H Pompe à plusieurs circuits
FR2532367B1 (fr) * 1982-08-24 1987-04-10 Bronzavia Sa Pompes a pistons axiaux solidaires de patins glissants sur une surface inclinee

Also Published As

Publication number Publication date
JP2527993B2 (ja) 1996-08-28
DE3862076D1 (de) 1991-04-25
EP0300274A1 (fr) 1989-01-25
DE3723988C2 (fr) 1989-06-01
JPS6441677A (en) 1989-02-13
US4852463A (en) 1989-08-01
DE3723988A1 (de) 1989-02-09

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