EP0220175B1 - Pompe hydraulique a pistons axiaux et a plateau oblique - Google Patents

Pompe hydraulique a pistons axiaux et a plateau oblique Download PDF

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Publication number
EP0220175B1
EP0220175B1 EP85902965A EP85902965A EP0220175B1 EP 0220175 B1 EP0220175 B1 EP 0220175B1 EP 85902965 A EP85902965 A EP 85902965A EP 85902965 A EP85902965 A EP 85902965A EP 0220175 B1 EP0220175 B1 EP 0220175B1
Authority
EP
European Patent Office
Prior art keywords
drum
bearing
force
cylinder
cylinder drum
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
Application number
EP85902965A
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German (de)
English (en)
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EP0220175A1 (fr
Inventor
Ingo Valentin
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Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AT85902965T priority Critical patent/ATE35719T1/de
Publication of EP0220175A1 publication Critical patent/EP0220175A1/fr
Application granted granted Critical
Publication of EP0220175B1 publication Critical patent/EP0220175B1/fr
Expired 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
    • F04B1/20—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
    • F04B1/2064—Housings
    • F04B1/2071—Bearings for cylinder barrels

Definitions

  • the invention relates to a hydraulic swash plate axial piston machine with a cylinder drum and pistons arranged in the cylinders of the cylinder drum, the piston heads of which are supported against the swash plate, while the cylinder drum is supported axially on a control mirror, the piston heads being adjacent to the useful torque related to the drum axis the cylinder drum also generate a radially acting drum shear force with a force application point lying in the drum axis, which shear force is absorbed by a bearing supporting the cylinder drum in the region of the drum shear force on the machine housing.
  • the cylinder drum has a collar on its outer circumference, which protrudes axially over the drum end face in the direction of the swash plate up to the plane perpendicular to the drum axis and intersecting the point of application of the drum transverse force.
  • the bearing supporting the cylinder drum in the form of a hydrodynamic plain bearing with cylindrical bearing surfaces. Thanks to this collar, the storage level, i. H.
  • the drum axis intersect directly in the area of the point of application of the drum lateral force, so that the support of the drum cylinder by the bearing also takes effect here, although the point of application of the drum lateral force in the plane running parallel to the swashplate through the centers of the piston heads and thus axially outside of the cylinder drum lies significantly in front of its face facing the swash plate.
  • the advantage of this drum bearing is that the drum shear force is unable to exert a tilting moment on the cylinder drum, which could result in a disturbing tilting of the cylinder drum on the control surface of a control disk, which controls the supply and discharge of the pressure medium to the cylinders of the cylinder drum and at which End face of the cylinder drum facing away from the swash plate, forming gap seals.
  • the collar and the bearing must include the swash plate and the row of piston sliding shoes that support the piston heads on the swash plate, which is undesirably large in the radial and axial direction and overall, also with regard to the pivotability of the Swashplate, complex constructions and due to the large diameter a greater loss of friction.
  • a swash plate axial piston machine which is provided as a double-acting arrangement with two swash plates, which face each other on both sides of the drum.
  • the pistons engaging the swash plates in pairs in the opposite direction are each arranged in common cylinders.
  • the pressure medium supply or discharge from the cylinder space is not possible from the front side of the drum, but takes place via pressure medium lines which open in the axial direction approximately in the middle of the cylinders and run radially there.
  • the cylinder drum In order to create the space required for this, the cylinder drum must have a correspondingly larger diameter, which leads to an undesirably large design in the radial direction and thus causes increased friction losses due to the large diameter.
  • the cylinder drum is supported by two bearings each approximately in the area of their end faces. Since the drum lateral forces act between the two bearings, tilting moments on the cylinder drum are safely absorbed. However, the second bearing causes further friction losses; In addition, the storage of the cylinder drum is determined in any case if its storage on the control mirror is also taken into account.
  • the cylinder drum also has a collar which projects axially over the end face of the drum in the direction of the swash plate up to the plane intersecting the point of application of the drum transverse force.
  • the collar is arranged on the inside here, that is to say in the region near the axis. As a result, the collar protrudes right up to the swashplate, which makes it difficult or even impossible to pivot. Therefore, the adjustability of the swash plate is not provided in this axial piston machine.
  • FR-A-1 599630 and FR-A-2115902 describe axial piston machines in which the cylinder drum is axially mounted approximately in the middle. The radial shear force acting on the drum therefore acts outside the bearing area and thus leads to an undesired tilting moment of the cylinder drum.
  • the object of the invention is to arrange and design the bearing of the cylinder drum in an axial piston machine of the type mentioned at the outset in such a way that even without an external encirclement of the swash plate and the piston sliding shoes, the cylinder drum is not supported by collars and bearings, and none on the cylinder drum or only causes tilting moments of such a small size that these residual moments can be absorbed by the control disk without disadvantage.
  • the plane of the bearing ie the plane of the bearing circle
  • the line of action of the resultants of all of them standing vertically on the guideway of the bearing Bearing forces include an acute angle with the drum axis and intersects the drum axis in the area of the point of application of the drum lateral force.
  • the bearing forces perpendicular to the guideway lie in the lateral surface of a cone, the tip of which can be thought of as the point of application of the individual bearing forces.
  • the base circle of the cone is formed by the bearing circle of the bearing and the cone tip lying in the drum axis either coincides with the point of application of the drum transverse force or is so close to it that the small distance between the drum transverse force and the resulting bearing force does not cause any disruptive tilting moments on the cylinder drum creates.
  • the height of the cone between the tip of the cone and the base circle of the cone is equal to the amount by which the bearing plane can be axially displaced away from the point of application of the drum transverse force towards the cylinder drum without the point of application of the resulting bearing force on the drum axis shifting accordingly and from the point of application of the Drum shear force removed.
  • the bearing itself can be moved axially far enough from the point of application of the drum lateral force and from the swash plate to the cylinder drum that it is axially far in front of the swash plate and in the area of the cylinder drum itself, and that therefore the bearing no longer needs to enclose the swash plate radially on the outside and also no longer a collar supporting the bearing is needed because the bearing can sit directly on the cylinder drum itself.
  • This enables small axial and radial dimensions and overall less construction and construction effort.
  • a preferred embodiment of the invention is characterized in that the guideway is formed by a conical ring surface, the cone tip of which lies in the drum axis on the same side of the force application point of the drum transverse force as the cylinder drum and which is so wide that the point of application of the drum transverse force is inside or at least tight next to the projection of the conical ring surface in the direction of its surface normal on the drum axis.
  • the conical ring surface should therefore be at least so wide that its projection onto the drum axis in any case includes the aforementioned periodic axial displacement of the point of application of the drum transverse force on the drum axis. Then each bearing support force applied in this point of attack always passes through the conical ring surface of the bearing.
  • the bearing can be designed as a hydrodynamically or hydrostatically acting slide bearing or as a tapered roller bearing.
  • the axial piston machines shown in the figures have a cylinder drum 2 connected to a shaft 1 and pistons 4 arranged in the cylinders 3.
  • the piston heads 5 are supported by sliding shoes 6 on the sliding surface of a swash plate 7, which is adjustable in the machine housing 8 with respect to its angle of inclination .
  • shaft 1 is a drive shaft in the case of a pump and an output shaft in the case of a motor. It is mounted in the machine housing 8 by means of a bearing 11.
  • the cylinder drum 2 is supported on the machine housing 8 in a further bearing 12.
  • the plane 13 of this bearing 12 intersects the drum axis 9 at a distance from the point of application 10 of the drum transverse force PkRes on the side of the cylinder drum 2.
  • the line of action 14 of the resulting bearing forces perpendicular to the guideway 15 of the bearing 12 forms an acute angle 26 with the drum axis 9 and cuts the drum axis 9 in the area of the point of application 10 of the drum lateral force PkRes.
  • the angle 26 is greater than approximately 60 °.
  • the bearing 12 can, as shown in FIG. 1 a, be a ball bearing, wherein the guideway 15 can be narrowed to a linear contact between the row of balls 16 on the one hand and the ball raceways 17 on the other. But mostly the guideway 15 will be formed by a conical ring surface, as shown in FIGS. 1, 2 and 3.
  • the conical tip 18 of this conical ring surface lies in the drum axis 9 on the same side of the force application point 10 as the cylinder drum 2.
  • the conical ring surface is otherwise so wide that the application point 10 of the drum transverse force PkRes within the projection of the conical in FIG Ring surface lies in the direction of its surface normal 19 on the drum axis 9.
  • the bearing 12 can be designed as a hydrodynamically or hydrostatically acting slide bearing, as shown in the figures in the right half of the figure, or as a tapered roller bearing, as shown in the figures on the left.
  • the bearing 12 is arranged directly between the outer peripheral surface 20 of the cylinder drum 2 and the housing jacket 2 of the machine housing 8 in the region of the end face 22 of the cylinder drum 2 facing the swash plate 7.
  • 2 and 3 show the case where the machine housing 8 has a pin 23, which is fixed to the machine housing and coaxial to the drum axis 9, between which and the cylinder drum 2 the bearing 12 is arranged.
  • the hollow pin 23 protrudes from the lower part of the machine housing 8 through the swash plate 7 to the cylinder drum 2 and receives the shaft 1.
  • the pin 23 arranged opposite to FIG. 2 engages through a central bore in the cylinder drum 2.
  • the cylinder drum 2 lies on its end face of the control surface facing away from the swash plate 7 of a control disc that controls the supply and removal of the conveying means to the cylinders 3 24 on. The supply and discharge of the funding takes place at the connections 25.

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

Abstract

La pompe comprend un tambour à cylindres (2) relié à un arbre (1) et muni de pistons (4) montés dans des cylindres (3). Les têtes (5) des pistons s'appuient sur un plateau oscillant (7) de façon que la force désignée par les pistons ne crée pas seulement un couple de rotation sur le tambour à cylindres (2), mais aussi une force transversale radiale (Pk Res), dont le point d'application (10) est situé dans l'axe (9) de l'arbre (1). Le plan (13) d'un roulement à rouleaux (12) interposé entre le bâti (8) et le tambour (2) intersecte l'axe (9) de l'arbre (1) a une certaine distance de ce point d'application (10). La droite (14) résultant de toutes les forces d'appui agissant perpendiculairement sur la droite de guidage (15) du roulement (12), forme un angle aigue (26) avec l'axe (9) et l'intersecte pratiquement au point d'application (10) de la force transversale (Pk Res) de façon que l'appui du tambour (2) se fasse sur ce point d'application et que des couples de renversement agissant sur le tambour soient évités.

Claims (7)

1. Machine hydraulique à pistons axiaux à plateau oblique, comportant un bloc-cylindres (2) et des pistons (4) disposés dans les cylindres (3) du bloc-cylindres (2) et dont les têtes (5) prennent appui contre le plateau oblique, tandis que le bloc-cylindres prend appui axialement sur une glace de distribution, les têtes des pistons produisant, en dehors du couple utile, rapporté à l'axe (9) du bloc-cylindres (2) et appliqué à ce dernier, également une force transversale radiale (PkRes) appliquée au bloc-cylindres, avec un point d'application (10) situé sur l'axe (9) du bloc-cylindres, cette force transversale étant supportée par un palier (12), qui supporte le bloc-cylindres (2) sur le carter (8) de la machine, au niveau de la force transversale (PkRes) appliquée au bloc-cylindres, caractérisée en ce que le plan (13) du palier (12) recoupe l'axe (9) du bloc-cylindres (2), à distance du point d'application (10) de la force transversale (PkRes) appliquée aux blocs-cylindres, et ce du côté de ce dernier, et que la droite d'action (14) de la résultante de toutes les forces de soutien perpendiculaires à la voie de guidage (15) du palier (12) fait un angle aigu (26) avec l'axe (9) du bloc-cylindres, et recoupe cet axe (9) au voisinage du point (10) d'application de la force transversale (PkRes) au bloc-cylindres.
2. Machine à pistons axiaux selon la revendication 1, caractérisée en ce que la voie de guidage (15) est formée par une surface annulaire conique, dont la pointe (18) du cône est située sur l'axe (9) du bloc-cylindres, du même côté du point (10) d'application de la force transversale (PkRes) au bloc-cylindres (2) que ce dernier, et est suffisamment large pour que le point (10) d'application de la force transversale (PkRes) au bloc-cylindres soit situé à l'intérieur ou au moins à proximité immédiate de la projection (X) de la surfaceannulaire conique dans la direction de la normale (19) de cette surface, sur l'axe (9) du bloc-cylindres.
3. Machine à pistons axiaux selon la revendication 1 ou 2, caractérisée en ce que le palier (12) est situé directement entre la surface périphérique extérieure (20) du bloc-cylindres (2) et l'enveloppe (21) du carter (8) de la machine au voisinage de la face frontale (22) du bloc-cylindres (2), tournée vers le plateau oblique (7).
4. Machine à pistons axiaux selon la revendication 1 ou 2, caractérisée en ce que le carter (8) de la machine comporte un embout (23) solidaire du carter de la machine et coaxial à l'axe (9) du bloc-cylindres et que le palier (12) est disposé entre cet embout (23) et le bloc-cylindres (2).
5. Machine à pistons axiaux selon la revendication 4, caractérisée en ce que l'embout (23) traverse le plateau oblique (16) en direction du bloc-cylindres (2) et est creux et que l'embout (23) loge un arbre (1 ) relié au bloc-cylindres (2).
6. Machine à pistons axiaux selon la revendication 4, caractérisée en ce que l'embout (23) s'étend à travers un perçage central du bloc-cylindres (2).
7. Machine à pistons axiaux selon l'une des revendications 2 à 6, caractérisée en ce que le palier (12) est réalisé sous la forme d'un palier lisse ou d'un roulement à rouleaux coniques.
EP85902965A 1984-06-26 1985-06-19 Pompe hydraulique a pistons axiaux et a plateau oblique Expired EP0220175B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85902965T ATE35719T1 (de) 1984-06-26 1985-06-19 Hydraulische axialkolbenmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3423467A DE3423467C2 (de) 1984-06-26 1984-06-26 Hydraulische Schiefscheiben-Axialkolbenmaschine
DE3423467 1984-06-26

Publications (2)

Publication Number Publication Date
EP0220175A1 EP0220175A1 (fr) 1987-05-06
EP0220175B1 true EP0220175B1 (fr) 1988-07-13

Family

ID=6239146

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85902965A Expired EP0220175B1 (fr) 1984-06-26 1985-06-19 Pompe hydraulique a pistons axiaux et a plateau oblique

Country Status (12)

Country Link
US (1) US4615257A (fr)
EP (1) EP0220175B1 (fr)
JP (1) JP2616764B2 (fr)
AU (1) AU4497785A (fr)
BR (1) BR8507206A (fr)
CA (1) CA1242931A (fr)
DD (1) DD243732A5 (fr)
DE (2) DE3423467C2 (fr)
ES (1) ES287634Y (fr)
MX (1) MX165040B (fr)
SU (1) SU1731068A3 (fr)
WO (1) WO1986000377A1 (fr)

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5490444A (en) * 1994-10-03 1996-02-13 Dynex/Rivett, Inc. Piston pump with improved hold-down mechanism
US5647266A (en) * 1994-10-03 1997-07-15 Dynex/Rivett, Inc. Hold-down mechanism for hydraulic pump
US5515768A (en) * 1995-02-28 1996-05-14 Caterpillar Inc. Slipper holddown device for an axial piston pump
US5862704A (en) * 1996-11-27 1999-01-26 Caterpillar Inc. Retainer mechanism for an axial piston machine
US7874914B2 (en) 1996-12-30 2011-01-25 Igt System and method for communicating game session information
US6406271B1 (en) * 1999-05-06 2002-06-18 Ingo Valentin Swashplate type axial-piston pump
DE19953766C1 (de) * 1999-11-09 2001-08-09 Danfoss As Hydraulische Axialkolbenmaschine
DE10055753B4 (de) * 1999-11-30 2013-11-28 Linde Hydraulics Gmbh & Co. Kg Hydrostatische Axialkolbenmaschine in Schrägscheibenbauweise mit Gleitschuhgelenken innerhalb der Bohrungen im Zylinderblock
DE10037927C2 (de) * 2000-08-03 2002-11-14 Sauer Danfoss Neumuenster Gmbh Hydromotor
DE10055262A1 (de) * 2000-11-08 2002-05-23 Linde Ag Hydrostatische Axialkolbenmaschine in Schrägscheibenbauweise
US6705203B2 (en) 2001-11-28 2004-03-16 Sauer-Danfoss Inc. Extended male slipper servo pad arrangement for positioning swashplate and method assembling same
DE10216951A1 (de) * 2002-04-17 2003-11-06 Bosch Rexroth Ag Hydrotransformator
DE102005021029A1 (de) * 2005-05-06 2006-11-09 Linde Ag Axialkolbenmaschine in Schrägscheibenbauweise mit Lagerung des Zylinderblocks auf einem Tragzapfen
CN100485164C (zh) * 2006-12-29 2009-05-06 郭有祥 陀螺轮转式引擎
DE102007048316B4 (de) * 2007-10-09 2010-05-27 Danfoss A/S Hydraulische Axialkolbenmaschine
US20090274564A1 (en) * 2008-04-30 2009-11-05 Caterpillar Inc. Floating cup pump having swashplate mounted cup elements
US20100028169A1 (en) * 2008-07-31 2010-02-04 Caterpillar Inc. Hydraulic device having an alignment component
US8333571B2 (en) * 2008-12-12 2012-12-18 Caterpillar Inc. Pump having pulsation-reducing engagement surface
KR101190076B1 (ko) 2010-03-24 2012-10-12 한국기계연구원 피스톤 펌프의 실린더배럴 베어링
US10574088B2 (en) 2010-04-28 2020-02-25 Energy Spring Ltd. Hydraulic based efficient renewable energy storage and regeneration system
US10533582B2 (en) 2010-04-28 2020-01-14 Energy Spring Ltd. Hydraulic based efficient energy storage and regeneration system
US10677354B2 (en) 2010-04-28 2020-06-09 Energy Spring Ltd. Hydraulic vehicle incorporating efficient energy storage and regeneration system
WO2012037738A1 (fr) * 2010-09-21 2012-03-29 华中科技大学 Pompe à eau à piston plongeur
NO20140581A1 (no) * 2013-05-26 2014-11-27 Subsea Hydraulic Components As Anordning og framgangsmåte ved pumpe for dykket anvendelse
CN104865060B (zh) * 2015-05-21 2017-04-12 浙江大学 一种多功能柱塞泵滑靴副油膜场参数测试试验台
MD1000Z (ro) * 2015-09-30 2016-10-31 Технический университет Молдовы Hidromotor precesional
FR3072736B1 (fr) * 2017-10-20 2022-05-06 Ifp Energies Now Pompe a barillet rotatif avec moyens de guidage et de centrage du barillet distincts
KR102249159B1 (ko) * 2019-06-14 2021-05-07 한국하이액트지능기술 주식회사 유체 펌프

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3124079A (en) * 1964-03-10 Jxanjacquxs j joyer
US2847984A (en) * 1955-11-07 1958-08-19 Gen Motors Corp Hydraulic engine-starting device
US2847938A (en) * 1955-12-01 1958-08-19 John T Gondek Hydraulic pump
FR1206702A (fr) * 1957-05-02 1960-02-11 New York Air Brake Co Moteur mû par un fluide sous pression
US3092034A (en) * 1959-02-18 1963-06-04 Kamper Motoren G M B H Axial piston engines
DE1175994B (de) * 1959-12-09 1964-08-13 Kaemper Motoren G M B H Axialkolbenmaschine
US3256782A (en) * 1963-02-19 1966-06-21 Ebert Heinrich Piston for hydraulic axial piston units with tiltable swash plate
CH417336A (de) * 1963-06-30 1966-07-15 Thoma Hans Prof Ing Dr Axialkolbenmaschine mit rotierendem Zylinderblock
DE1269494B (de) * 1964-10-24 1968-05-30 Bosch Gmbh Robert Einrichtung zum Andruecken der Kolbengleitschuhe an die Schiefscheibe einer Druckfluessigkeits-Axialkolbenmaschine
FR1469527A (fr) * 1965-12-03 1967-02-17 Messier Fa Pompe ou moteur hydraulique à barillet tournant
FR1488511A (fr) * 1966-07-25 1967-07-13 Boulton Aircraft Ltd Perfectionnements aux pompes et moteurs hydrauliques
FR1599630A (fr) * 1968-09-26 1970-07-15
US3861276A (en) * 1970-03-03 1975-01-21 Messier Sa Hydraulic rotary barrel pumps or motors
US3747476A (en) * 1970-03-31 1973-07-24 Delavan Manufacturing Co Balanced hydraulic device
DE2057926A1 (de) * 1970-11-25 1972-06-08 Schaeffler Ohg Industriewerk Axialkolbenpumpe
GB1593731A (en) * 1976-07-26 1981-07-22 Secretary Industry Brit Axial piston hydraulic machines

Also Published As

Publication number Publication date
MX165040B (es) 1992-10-13
AU4497785A (en) 1986-01-24
WO1986000377A1 (fr) 1986-01-16
JPS61502551A (ja) 1986-11-06
DE3423467A1 (de) 1986-01-02
US4615257A (en) 1986-10-07
EP0220175A1 (fr) 1987-05-06
DE3563772D1 (en) 1988-08-18
DE3423467C2 (de) 1986-04-24
CA1242931A (fr) 1988-10-11
SU1731068A3 (ru) 1992-04-30
ES287634Y (es) 1987-01-16
DD243732A5 (de) 1987-03-11
JP2616764B2 (ja) 1997-06-04
BR8507206A (pt) 1987-08-04
ES287634U (es) 1986-05-01

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