EP0697520B1 - 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 PDFInfo
- Publication number
- EP0697520B1 EP0697520B1 EP95112878A EP95112878A EP0697520B1 EP 0697520 B1 EP0697520 B1 EP 0697520B1 EP 95112878 A EP95112878 A EP 95112878A EP 95112878 A EP95112878 A EP 95112878A EP 0697520 B1 EP0697520 B1 EP 0697520B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- ball head
- bearing surface
- plane
- bearing
- 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
Links
- 230000002706 hydrostatic effect Effects 0.000 title claims description 11
- 230000005484 gravity Effects 0.000 claims description 7
- 238000006073 displacement reaction Methods 0.000 description 6
- 210000003734 kidney Anatomy 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
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 it 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 runs in a plane E 2 perpendicular to the piston axis L K and has two open ends, with which it opens into the cylindrical surface 32 or into 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 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 obliquely.
- 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)
Claims (4)
- Tête sphérique (K), qui soutient directement ou indirectement un piston (25) d'une machine hydrostatique à piston axial ou radial sous décharge hydrostatique contre son corps mobile (13), la tête sphérique étant prévue dans une portion de sphère creuse (KA), limitée par une ouverture circulaire (29), et présentant une surface de cylindre (32), qui s'étend des deux côtés d'une ligne d'équateur (Q), formant avec l'axe (LK) du piston, un angle (β) différent de 90°, présente un plus petit diamètre que l'ouverture circulaire délimitant la portion de sphère creuse et une calotte sphérique (KK) sur la tête sphérique pour le montage dans une surface de palier (35) de la portion de sphère creuse, caractérisée en ce que dans la calotte sphérique (KK) ou dans la surface de palier (35) est formée une rainure de décharge (33) ouverte à ses deux extrémités, qui débouche avec ses extrémités ouvertes toujours dans la cavité (34) délimitée par la surface de cylindre (32) et par la surface de palier (35) et délimite, dans la calotte sphérique (KK), une contre-surface de palier (36), soutenue par décharge hydrostatique contre la surface de palier (35), dont le centre de gravité de surface (F) se situe toujours dans la zone de l'axe (LK) du piston.
- Tête sphérique selon la revendication 1, caractérisée en ce que la rainure de décharge (33) s'étend dans un plan (E2) perpendiculaire à l'axe (LK) du piston.
- Tête sphérique selon la revendication 1, caractérisée en ce que la rainure de décharge (33) s'étend dans un plan perpendiculaire au plan (E2).
- Tête sphérique selon la revendication 1, caractérisée en ce que la rainure de décharge (33) s'étend dans un plan qui est perpendiculaire au plan dans lequel se situe la ligne d'équateur (Q).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4429053A DE4429053C1 (de) | 1994-08-16 | 1994-08-16 | Kugelkopf zur Abstützung eines Kolbens einer hydrostatischen Axial- oder Radialkolbenmaschine an deren Hubkörper |
DE4429053 | 1994-08-16 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0697520A1 EP0697520A1 (fr) | 1996-02-21 |
EP0697520B1 true 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 (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014104951A1 (de) | 2014-04-08 | 2015-10-08 | Linde Hydraulics Gmbh & Co. Kg | Axialkolbenmaschine in Schrägachsenbauweise |
Families Citing this family (10)
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 |
CN105339657B (zh) * | 2013-05-22 | 2018-01-12 | 贺德克传动中心有限公司 | 以斜盘式结构形式的轴向活塞泵 |
CN104074738B (zh) * | 2014-06-30 | 2017-03-22 | 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 |
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 |
IT201900001613A1 (it) * | 2019-02-05 | 2020-08-05 | Dana Motion Sys Italia Srl | Pistone per macchine idrauliche a pistoni assiali. |
Family Cites Families (5)
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 |
DE2358870B2 (de) * | 1973-11-26 | 1980-02-21 | Hydromatik Gmbh, 7900 Ulm | Axialkolbenmaschine mit einstuckigem Kolben |
US5114261A (en) * | 1989-07-31 | 1992-05-19 | Honda Giken Kogyo Kabushiki Kaisha | Swashplate type hydraulic device having a ball joint connection |
DE4214765A1 (de) * | 1992-05-04 | 1993-11-11 | Sachsenhydraulik Gmbh | Kolben-Gleitschuh Verbindung für hydro-statische Maschinen |
-
1994
- 1994-08-16 DE DE4429053A patent/DE4429053C1/de not_active Expired - Fee Related
-
1995
- 1995-08-16 EP EP95112878A patent/EP0697520B1/fr not_active Expired - Lifetime
- 1995-08-16 DE DE59500767T patent/DE59500767D1/de not_active Expired - Fee Related
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014104951A1 (de) | 2014-04-08 | 2015-10-08 | Linde Hydraulics Gmbh & Co. Kg | Axialkolbenmaschine in Schrägachsenbauweise |
EP2940299A2 (fr) | 2014-04-08 | 2015-11-04 | Linde Hydraulics GmbH & Co. KG | Machine à piston axial dans une construction à axe oblique |
Also Published As
Publication number | Publication date |
---|---|
DE59500767D1 (de) | 1997-11-13 |
DE4429053C1 (de) | 1995-11-02 |
EP0697520A1 (fr) | 1996-02-21 |
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