EP0220175A1 - Pompe hydraulique a pistons axiaux et a plateau oblique. - Google Patents

Pompe hydraulique a pistons axiaux et a plateau oblique.

Info

Publication number
EP0220175A1
EP0220175A1 EP85902965A EP85902965A EP0220175A1 EP 0220175 A1 EP0220175 A1 EP 0220175A1 EP 85902965 A EP85902965 A EP 85902965A EP 85902965 A EP85902965 A EP 85902965A EP 0220175 A1 EP0220175 A1 EP 0220175A1
Authority
EP
European Patent Office
Prior art keywords
drum
bearing
cylinder
cylinder drum
point
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
EP85902965A
Other languages
German (de)
English (en)
Other versions
EP0220175B1 (fr
Inventor
Ingo Valentin
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.)
Individual
Original Assignee
Individual
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 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

Links

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

  • Hydraulic sliding disc axial piston machine Hydraulic sliding disc axial piston machine.
  • 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, so that the piston forces in addition to the useful torque on the cylinder drum related to the drum axis generate a radially acting drum transverse force with a force application point lying in the drum axis, and with a bearing supporting the cylinder drum in the region of the drum lateral force on the machine housing.
  • the cylinder drum has a collar on its outer circumference, which protrudes axially beyond the drum end face in the direction of the swashplate 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. cut the plane of the bearing circle, the drum axis directly in the area of the point of application of the drum lateral force, so that the support of the drum
  • spare sheet mel cylinder becomes effective through the bearing, although the point of application of the drum lateral force in the plane parallel to the swash plate through the centers of the piston heads and thus axially outside the cylinder drum lies considerably in front of its end facing the swash plate.
  • This drum bearing arrangement is that the drum transverse force is unable to exert any tilting moments on the cylinder drum, which could result in a disruptive tilting of the cylinder drum on the control surface of a control disk, which leads to the supply and discharge of the pressure medium to the cylinders Controls the cylinder drum and rests on the end face of the Zyllnder drum facing away from the slant plate, forming gap seals, but it is disadvantageous in such a bearing arrangement that the collar and the bearing hold the slant plate and the row of piston sliding shoes supporting the piston heads on the slant plate Outside must include what undesirably large designs in the radial and axial direction and overall, also with regard to the pivotability of the slide washer, complex constructions and due to the large diameter a greater loss of friction.
  • 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 the cylinder drum is supported by collars and bearings without an external encirclement of the swash plate and the piston sliding shoes no or only small tilting moments can occur on the cylinder drum, that these residual moments can be absorbed by the control disc without disadvantage.
  • the plane of the bearing ie the plane of the bearing circle
  • the line of action of the resultant of all affects perpendicular to the guideway of the bearing bearing forces forms an acute angle with the drum axis and intersects the drum axis in the area of the point of application of the drum transverse 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 attack for the resultant of all 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 ⁇ dertrommel creates.
  • the height of the cone between the cone tip and the base circle of the cone is equal to the extent to 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 being shifted accordingly and from the point of application of the drum lateral force.
  • bearing support of the cylinder drum becomes axially the bearing itself so far from the point of application of the drum transverse force and from the swash plate to the cylinder drum that it lies axially far in front of the swash plate and in the area of the cylinder drum itself, and therefore the bearing No longer needs to include the swash plate radially on the outside and also no longer needs the collar supporting the bearing, because the bearing can sit directly on the cylinder drum itself. This enables small axial and radial dimensions and an overall lower design and construction effort.
  • angles of more than 60 ° between the resultant of the bearing forces and the drum axis are only a few percent of the axial forces to be absorbed and compensated for on the cylinder drum, which are directly exerted by the pressure of the conveying means on the cylinder drum.
  • 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 within or is at least close to the projection of the conical ring surface in the direction of its surface normal onto 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 attack of the drum transverse force on the drum axis. Then each bearing support force applied at this point of attack always passes through the conical ring surface of the bearing.
  • the bearing directly between the outer circumferential surface of the cylinder drum and the housing jacket of the machine housing in the region of the end face of the cylinder drum facing the slant plate.
  • the cylinder drum also has the option of internal storage.
  • the machine housing has a pin which is fixed to the machine housing and coaxial with the drum axis, and in that the bearing is arranged between this pin and the cylinder drum.
  • the pin can pass through the swash plate towards the cylinder drum and can be hollow so that it can receive a shaft connected to the cylinder drum.
  • the pin can also reach from the other end of the machine housing through a central bore in the cylinder drum.
  • the bearing can be designed as a hydrodynamically or hydrostatically acting slide bearing or as a tapered roller bearing.
  • FIG. 1 shows a swash plate axial piston machine according to the invention in an axial section, with a further bearing design shown in the partial figure 1a,
  • FIG. 2 shows another embodiment of the machine according to the invention in a representation corresponding to FIG. 1, "
  • Fig. 3 shows another embodiment of the invention.
  • the axial piston machines shown in the figures have a cylinder connected to a shaft 1. drum 2 and arranged in the cylinders 3 piston 4.
  • the piston heads 5 are supported via sliding blocks 6 on the sliding surface of a sliding disc '7, 8 is supported their inclination angle with respect to the housing schin adjustable in Ma ⁇ .
  • 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 which are perpendicular to the guideway 15 of the bearing 12 closes an acute angle 26 with the drum axis 9 and intersects the drum axis 9 in the region of the point of application 10 of the drum transverse force PkRes.
  • the angle 26 is greater than approximately 60 °. As shown in FIG.
  • the bearing 12 can be a ball bearing, wherein the guide track 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 hand.
  • the guideway 15 will be formed by a conical ring surface, as shown in FIGS. 1, 2 and 3.
  • the cone 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 lateral force PkRes is within the range shown in FIG. * Projection of the conical ring surface, designated X, 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 circumferential surface 20 of the cylinder drum 2 and the housing shell 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 in which the machine housing 8 has a pin 23 fixed to the machine housing and coaxial to the drum axis 9, between which and the cylinder drum 2 the bearing 12 is arranged, - * in FIG hollow pin 23 from the lower part of the machine housing 8 through the slant plate 7 to the cylinder drum 2 and receives the shaft 1.
  • the pin 23 arranged opposite to FIG. 2 engages through a central one Bore of the cylinder drum 2.
  • the cylinder drum 2 rests on its end of the control surface facing away from the slanting disc 7 of a control disc 24 which controls the supply and discharge of the conveying means to the cylinders 3.
  • the supply and delivery of the funding takes place at the connections 25 *

Landscapes

  • 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.
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 true EP0220175A1 (fr) 1987-05-06
EP0220175B1 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
US5647266A (en) * 1994-10-03 1997-07-15 Dynex/Rivett, Inc. Hold-down mechanism for hydraulic pump
US5490444A (en) * 1994-10-03 1996-02-13 Dynex/Rivett, Inc. Piston pump with improved hold-down mechanism
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
US10677354B2 (en) 2010-04-28 2020-06-09 Energy Spring Ltd. Hydraulic vehicle incorporating efficient energy storage and regeneration system
US10533582B2 (en) 2010-04-28 2020-01-14 Energy Spring Ltd. Hydraulic based efficient energy storage and regeneration system
US10574088B2 (en) 2010-04-28 2020-02-25 Energy Spring Ltd. Hydraulic based efficient renewable 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
US2925046A (en) * 1957-05-02 1960-02-16 New York Air Brake Co Engine
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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8600377A1 *

Also Published As

Publication number Publication date
DE3423467A1 (de) 1986-01-02
JP2616764B2 (ja) 1997-06-04
WO1986000377A1 (fr) 1986-01-16
DE3563772D1 (en) 1988-08-18
CA1242931A (fr) 1988-10-11
EP0220175B1 (fr) 1988-07-13
SU1731068A3 (ru) 1992-04-30
DD243732A5 (de) 1987-03-11
MX165040B (es) 1992-10-13
AU4497785A (en) 1986-01-24
JPS61502551A (ja) 1986-11-06
ES287634Y (es) 1987-01-16
US4615257A (en) 1986-10-07
ES287634U (es) 1986-05-01
BR8507206A (pt) 1987-08-04
DE3423467C2 (de) 1986-04-24

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