EP0162238B1 - Axial piston machine, especially a pump of the inclined plate type - Google Patents

Axial piston machine, especially a pump of the inclined plate type Download PDF

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Publication number
EP0162238B1
EP0162238B1 EP85103801A EP85103801A EP0162238B1 EP 0162238 B1 EP0162238 B1 EP 0162238B1 EP 85103801 A EP85103801 A EP 85103801A EP 85103801 A EP85103801 A EP 85103801A EP 0162238 B1 EP0162238 B1 EP 0162238B1
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EP
European Patent Office
Prior art keywords
control surface
cylinder
loading
axial piston
pistons
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
EP85103801A
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German (de)
French (fr)
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EP0162238A1 (en
Inventor
Ludwig Wagenseil
Manfred Lotter
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Hydromatik GmbH
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Hydromatik GmbH
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Publication of EP0162238A1 publication Critical patent/EP0162238A1/en
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    • 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
    • F04B1/2007—Arrangements for pressing the cylinder barrel against the valve plate, e.g. by fluid pressure
    • 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
    • F04B1/2042—Valves
    • 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 an axial piston machine according to the preamble of claim 1.
  • GB-A-311 938 An axial piston machine of the type described at the outset is described and shown in GB-A-311 938.
  • the cylinder rests with a flat end face on a flat control surface, the piston bores opening on the end face without narrowing in cross section.
  • load cylinders are arranged on the circumference of the cylinder, which are connected to the piston bores and can thus be acted upon by the working pressure and act on the cylinder against the control surface.
  • the cylinder is mounted on the drive shaft of a swash plate axial piston machine in the sense of a so-called kinematic guide.
  • each loading cylinder is connected by a connecting channel to a piston bore located in its vicinity.
  • the cylinder is supported by a roller bearing, which prevents an automatic gap adjustment.
  • the invention has for its object to design an axial piston machine of the type mentioned in such a way that axially and radially balanced guidance of the cylinder is possible with maximum utilization of the piston powers.
  • a spherical control surface leads to a radial force component, but the radial force component is harmless in the embodiment according to the invention because it acts in a transverse plane of the axial piston machine, in which the cylinder is supported radially and thus cannot exert a tilting moment on the cylinder.
  • the cylinder is freed of significant damaging forces both axially and radially. This leads to an optimal contact of the cylinder on the spherical control surface, whereby an effective oil film can form between the control surface and the cylinder due to the balance of the control surface force and the load force, whereby friction and wear are minimized.
  • both the loading force and the control surface force can consist of several partial forces, e.g. B. the frictional forces acting in the displacement of the pistons in both axial directions also influence both the control surface force and the loading force.
  • the cylinder by a central spring force, for. B. in the form of a compression spring, constantly applied against the pressure surface, as is the case with the prior art according to DE-OS 22 50 510.
  • the partial force generated by the spring is part of the loading force.
  • the embodiment according to claim 2 is advantageous for two reasons. On the one hand, due to the piston path tapering conically to the control surface, there is a smaller radius for the control openings in the control surface. As a result, due to a relatively small pressure field and the shorter lever arm, the partial forces of the control surface force caused are lower, which enables smaller loading cylinders. On the other hand, space is gained for the loading cylinders due to this configuration.
  • a load cylinder is assigned to each piston, wherein there is a line connection between the associated piston bores and load cylinders.
  • the embodiment according to claim 7 leads to an adaptation of the balancing force generated by the loading cylinder to the actual pressure profile in the piston chambers, which is due to structural and natural law conditions relative to the cylinder in the circumferential direction, so to speak, out of phase.
  • the axial piston machine which can be operated as a pump and as a motor, consists of a housing generally designated 2, a drive shaft 4, which is rotatably mounted therein about an axis of rotation 3, a so-called swash plate 5, on which by means of sliding shoes 6 and a pressure plate 7, pistons 8 are held distributed on a pitch circle, a cylinder 9 rotatable by the drive shaft 4 about the axis of rotation 3, in which the pistons 8 are displaceably guided in axially extending piston bores 11 and a control plate 12 immovably attached to the housing 2 , whose spherically convexly curved control surface 13 has kidney-shaped control openings 14 which, during the rotation of the cylinder 9, come into or out of overlap with the piston bores 11 and thus control the pumping operation or motor operation of the axial piston machine 1 in the sense of valves.
  • the pistons 8 are driven by the swash plate 5, on which the pistons 8 are only held axially. That is, while the cylinder 9 is rotating, the sliding shoes 6 slide circumferentially on the swash plate 5, whereby the axial movement of the pistons 8 is generated.
  • the end face of the cylinder 9 facing the control surface 13 is spherically concave in accordance with the curvature of the control surface 13 and lies sealingly against the control surface 13.
  • the cylinder 9 has a bore 15 in which it is penetrated by the drive shaft 4 with play, which is supported in the region of its ends by means of roller bearings 16 and 17.
  • the cylinder 9 is supported only on its end facing away from the control surface 13 by a radially effective support bearing 18 on the drive shaft 4.
  • a rotary driving connection 19 in the form of a keyway connection which is effective in the circumferential direction.
  • the cylinder 9 is biased by one or more compression springs 21 against the control surface 13, which act against the end face of the cylinder 9 facing away from the control surface 13 and are supported on a spherical bearing part 22 which, on the one hand, engages around the cylinder 9 with a cylindrical bore and on whose outer spherical surface slidably slides the pressure plate 7.
  • the support bearing 18 is arranged in the area of a plane denoted by A, which is also the central swivel plane of the swash plate 5.
  • a control surface force which acts perpendicular to the control surface 13 and attempts to lift the cylinder 9 from the control surface 13 acts on the cylinder 9, and an axially directed, resulting load force, generally designated F ER , which Cylinder 9 acted against the control surface 13.
  • the control surface force F s results essentially as the sum of the partial pressures over the entire pressure field and possible gap pressures which are able to build up between the control surface 13 and the end face 23 of the cylinder 9 sliding thereon and which attempt to lift the cylinder 9 off the control surface 13 .
  • several partial forces have an influence, e.g. B.
  • the resulting loading force F ER likewise comprises several partial forces and in particular a loading force F E with which loading cylinders 24 distributed over the circumference act on the cylinder 9 in the direction of the control surface 13.
  • the resulting loading force F ER also generally includes piston forces denoted by F K , which, as in the explanation of the control surface force Fs, will not be discussed further.
  • the force, not specified, generated by the compression springs 21 also influences the resulting loading force F ER .
  • the pistons of the loading cylinder 24 are designated 25 and the associated work spaces 26.
  • a load cylinder 24 is assigned to each piston 8, the piston bores 11 being connected to the associated working spaces 26 of the load cylinders 24 by radial channels 27.
  • the loading pistons 25 are supported on the housing 2 by means of a slide ring 28. They are pierced at 31 for the purpose of automatic lubrication of the sliding surface 29. While the slide ring 28 is fixedly attached to the housing 2, the loading pistons 25 take part in the rotary movement of the cylinder 9.
  • the cylinder 9 has a flange 32 for receiving the loading cylinders 24.
  • Both the control surface force F s and the loading force F E generated by the loading cylinders 24 are pulsating forces. This results from the pressure build-up or drop in the piston bores 11.
  • control surface force F s Since the control surface force F s is not directed parallel to the axis of rotation 3, its control surface force component F SK directed parallel to the axis of rotation 3 is lower.
  • the forces acting in opposite directions on the cylinder 9 are in equilibrium. If one takes into account that the control surface force component F SK has a smaller distance a from the axis of rotation 3 than the resulting load force F ER , the distance of which from the axis of rotation 3 is denoted by b, then the result is a relatively smaller size in comparison with the control surface force component F SK Load force F ER to create a balance of forces. In order to achieve this balance of forces, the working surfaces (diameter d) of the loading cylinder 24 are designed accordingly.
  • a radially directed force component F R results which radially loads the cylinder 9.
  • the radius R of the control surface 13 is dimensioned so large that the lines of force of the control surface force F s and the resulting loading force F ER intersect at a point S which lies on the transverse plane A in which the cylinder 9 is supported radially. Due to this configuration, the radial force component F R is unable to exert a tilting moment on the cylinder 9.
  • the embodiment of the second exemplary embodiment according to FIG. 2 differs from the first exemplary embodiment only in that the axes of the pistons 8 converge in the direction of the control surface 13. As a result, the pistons 8 are rotated on a path which tapers conically towards the control surface 13. In such an embodiment, the size of the pressure field is compared to the first embodiment
  • the loading force F ER is directed somewhat obliquely in contrast to the first embodiment.
  • the same force relationships as in the first exemplary embodiment result in the second exemplary embodiment.
  • the third exemplary embodiment according to FIG. 3 differs from the second exemplary embodiment essentially in that no compression springs are provided which act on the cylinder 9 in the direction of the control surface 13 and which are designated 21 in FIG. 1. Instead, corresponding springs 21 are provided in the load cylinders, where they both cause the pistons 24 to lift up in the unpressurized state and also cause the cylinder 9 to effectively rest against the spherical control surface. A certain investment power is not harmful if it is low.
  • FIG. 4 and 5 show a cross-section rotated by 90 ° alternately through the axial piston machine according to FIG. 1 along the line IV-IV or in the plane of the connecting channels 27. It should be taken into account that FIG. 5 is a relative to the Fig. 4 shows a modified embodiment as a fourth embodiment.
  • the control surface 13 is indicated by dashed lines.
  • the kidney shape of the control openings 14, also shown with dashed lines, is clearly recognizable.
  • the fourth exemplary embodiment according to FIG. 5 differs from the first exemplary embodiment according to FIG. 4 in that the pressure field 33 of the control surface 13 indicated with cross hatching is rotated by a certain angle w against the dead center axis 34.
  • the loading cylinders 24 are prematurely rotated in the same circumferential direction (see direction of rotation 35) by an angle w 1 .
  • the loading force F E also has a leading effect in adaptation to the pressure build-up or reduction in the piston chambers 11.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)

Description

Die Erfindung bezieht sich auf eine Axialkolbenmaschine nach dem Oberbegriff des Anspruchs 1.The invention relates to an axial piston machine according to the preamble of claim 1.

Bei Axialkolbenmaschinen dieser Bauart ist ein sauberer Lauf und eine befriedigende Abdichtung des die Kolben aufnehmenden Zylinders auf der Steuerfläche nur dann gegeben, wenn die auf den Zylinder im Betrieb wirkenden Kräfte so bemessen sind, daß einerseits ein auch nur teilweises Abheben des Zylinders von der Steuerfläche verhindert ist und zum anderen ein Andruck des Zylinders an die Steuerfläche vorliegt, bei dem sich ein einen erhöhten Verschleiß verhindernder Ölfilm auf der Steuerfläche ausbilden kann. Im vorliegenden Zusammenhang sollen zunächst die Kräfte Berücksichtigung finden, die in axialer Richtung auf den Zylinder wirken. Es handelt sich zum einen um eine sogenannte Steuerflächenkraft, die im Betrieb den Zylinder von der Steuerfläche abzuheben sucht. Die Steuerflächenkraft ergibt sich als Summe der partialen Drücke und Fläche über dem gesamten Druckfeld und möglichen Spaltdrücken. Deshalb wird die Steuerflächenkraft durch eine resultierende Kraft dargestellt, die senkrecht zur Steuerfläche gerichtet ist.In axial piston machines of this type, a smooth running and a satisfactory sealing of the cylinder receiving the pistons on the control surface is only possible if the forces acting on the cylinder during operation are dimensioned such that on the one hand even a partial lifting of the cylinder from the control surface is prevented and on the other hand there is a pressure of the cylinder on the control surface, in which an oil film preventing increased wear can form on the control surface. In the present context, the forces that act on the cylinder in the axial direction should first be taken into account. On the one hand, it is a so-called control surface force that tries to lift the cylinder from the control surface during operation. The control surface force is the sum of the partial pressures and area over the entire pressure field and possible gap pressures. Therefore, the control surface force is represented by a resulting force that is perpendicular to the control surface.

Eine Axialkolbenmaschine der eingangs bezeichneten Bauart ist in der GB-A-311 938 beschreiben und dargestellt. Bei dieser bekannten Ausgestaltung liegt der Zylinder mit einer ebenen Stirnfläche an einer ebenen Steuerfläche an, wobei die Kolbenbohrungen ohne Querschnittsverengung an der Stirnseite münden. Zur Kompensation der Steuerflächenkraft sind auf dem Umfang des Zylinders verteilt Belastungszylinder angeordnet, die mit den Kolbenbohrungen verbunden und somit mit dem Arbeitsdruck beaufschlagbar sind und den Zylinder gegen die Steuerfläche beaufschlagen.An axial piston machine of the type described at the outset is described and shown in GB-A-311 938. In this known embodiment, the cylinder rests with a flat end face on a flat control surface, the piston bores opening on the end face without narrowing in cross section. To compensate for the control surface force, load cylinders are arranged on the circumference of the cylinder, which are connected to the piston bores and can thus be acted upon by the working pressure and act on the cylinder against the control surface.

Aus der DE-OS 2 250 510 ist es ebenfalls bekannt, der Steuerflächenkraft durch eine entgegengesetzte Belastungskraft entgegenzuwirken, die den Zylinder gegen die Steuerfläche beaufschlagt. Dies wird durch mehrere Maßnahmen erreicht. Zum einen weisen die Kolbenbohrungen eine durch eine Querschnittsverringerung gebildete Schulter auf, an der ein Teil der Belastungskräfte wirksam ist. Ein anderer Teil der Belastungskräfte wird durch auf dem Umfang verteilte Belastungskolben erzeugt, die am Maschinengehäuse abgestützt sind, die entweder durch Federdruck oder als hydraulische Kolben vom Arbeitsdruck beaufschlagbar sind und den Zylinder in Richtung auf die Steuerfläche belasten. Außerdem ist eine zentrale Feder vorhanden, die den Zylinder gegen die Steuerfläche vorspannt.From DE-OS 2 250 510 it is also known to counteract the control surface force by an opposing loading force which acts on the cylinder against the control surface. This is achieved through several measures. On the one hand, the piston bores have a shoulder formed by a reduction in cross section, on which part of the loading forces is effective. Another part of the load forces is generated by load pistons distributed over the circumference, which are supported on the machine housing and can be acted upon by the working pressure either by spring pressure or as hydraulic pistons and load the cylinder in the direction of the control surface. There is also a central spring that biases the cylinder against the control surface.

Beim aus DE-OS 2 250 510 entnehmbaren Stand der Technik ist der Zylinder im Sinne einer sogenannten kinematischen Führung auf der Antriebswelle einer Schrägscheiben-Axialkolbenmaschine gelagert. D.h., der Zylinder vermag sich selbsttätig an die Steuerfläche anzupassen, jedoch sind grundsätzlich auch Kippbewegungen des Zylinders möglich, die - wie eingangs schon beschrieben - zu einem Abheben des Zylinders von der Steuerfläche führen.In the prior art which can be gathered from DE-OS 2 250 510, the cylinder is mounted on the drive shaft of a swash plate axial piston machine in the sense of a so-called kinematic guide. This means that the cylinder can adapt itself to the control surface, but in principle tilting movements of the cylinder are also possible, which - as already described at the beginning - lead to the cylinder being lifted off the control surface.

Ein mit dem vorbeschriebenen Stand der Technik vergleichbarer Stand der Technik ist auch aus DE-PS 941 343 zu entnehmen. Bei dieser Bauart ist die Wirksamkeit der Beiastungs- bzw. Ausgleichszylinder vom Druckzustand in den Kolbenbohrungen abhängig. Hierzu ist jeder Belastungszylinder durch einen Verbindungskanal mit einer in seiner Nähe befindlichen Kolbenbohrungen verbunden. Der Zylinder ist mittels eines Wälzlagers gelagert, was eine selbsttätige Spaltanpassung verhindert.A prior art comparable to the previously described prior art can also be found in DE-PS 941 343. With this type of construction, the effectiveness of the load or compensating cylinders depends on the pressure condition in the piston bores. For this purpose, each loading cylinder is connected by a connecting channel to a piston bore located in its vicinity. The cylinder is supported by a roller bearing, which prevents an automatic gap adjustment.

Bei den vorbeschriebenen, bekannten Bauarten, bei denen die Querschnittsverengungen der Kolbenbohrungen Durchflußengpässe bilden, ist der jeweilige Strom des hydraulischen Mediums beeinträchtigt. Außerdem sind die eingangs beschriebenen Forderungen nicht erfüllt, die eine einwandfreie Führung des Zylinders auf der Steuerfläche gewährleisten. Bei der Bauart gemäß DE-PS 941 343 scheint ein schädlicher Andruck des Zylinders an die Steuerfläche nicht möglich zu sein, weil der Zylinder stirnseitig gegen ein Axialdrucklager abgestützt ist.In the known designs described above, in which the cross-sectional constrictions of the piston bores form flow bottlenecks, the respective flow of the hydraulic medium is impaired. In addition, the requirements described at the outset are not met, which ensure that the cylinder is properly guided on the control surface. In the design according to DE-PS 941 343, a harmful pressure of the cylinder against the control surface does not seem to be possible because the cylinder is supported on the end face against an axial pressure bearing.

Es ist aus der DE-C-910 239 bekannt, zur Abstützung des Zylinders eine konvexe Steuerfläche vorzusehen, wobei der Radius der Steuerfläche so groß bemessen ist, daß der Schnittpunkt der senkrecht zur Steuerfläche gerichteten Steuerflächenkraft und der Belastungskraft in einer quer zur Drehachse verlaufenden Ebene liegt, die im Bereich eines am Zylinderumfang vorgesehenen Stützlagers angeordnet ist. Bei dieser Ausgestaltung sind jedoch keine Belastungszylinder sondern nur Querschnittsverengungen der Kolbenbohrungen vorgesehen, die radialeinwärts versetzt und somit auf einem verhältnismäßig kleinen Teilkreis angeordnet sind.It is known from DE-C-910 239 to provide a convex control surface for supporting the cylinder, the radius of the control surface being dimensioned so large that the intersection of the control surface force directed perpendicular to the control surface and the loading force in a plane running transversely to the axis of rotation lies, which is arranged in the region of a support bearing provided on the cylinder circumference. In this embodiment, however, no load cylinders are provided, but only cross-sectional constrictions of the piston bores, which are offset radially inward and are therefore arranged on a relatively small pitch circle.

Der Erfindung liegt die Aufgabe zugrunde, eine Axialkolbenmaschine der eingangs bezeichneten Bauart so auszugestalten, daß bei maximaler Ausnutzung der Kolbenleistungen eine axial und radial ausgeglichene Führung des Zylinders möglich ist.The invention has for its object to design an axial piston machine of the type mentioned in such a way that axially and radially balanced guidance of the cylinder is possible with maximum utilization of the piston powers.

Diese Aufgabe wird durch die Merkmale des Anspruchs 1 gelöst.This object is solved by the features of claim 1.

Bei der sphärischen Wölbung der Steuerfläche sind die aufgrund des Druckfeldes und der Spaltdrücke an der Steuerfläche hervorgerufenen Teilkräfte der Steuerflächenkraft senkrecht zur Steuerfläche gerichtet, und deshalb sind die parallel zu den Kolben gerichteten Komponenten dieser Teilkräfte geringer. Dies ist eine günstige Auswirkung, da bei der Bemessung der Belastungskraft nur die parallel zu den Kolben gerichtete Komponente der Steuerflächenkraft zuIn the case of the spherical curvature of the control surface, the partial forces of the control surface force caused on the control surface due to the pressure field and the gap pressures are directed perpendicular to the control surface, and therefore the components of these partial forces directed parallel to the pistons are lower. This is a favorable effect, because when designing the loading force only the component of the control surface force directed parallel to the piston is added

berücksichtigen ist. Eine sphärische Steuerfläche führt zwar zu einer radialen Kraftkomponente, jedoch ist die radiale Kraftkomponente bei der erfindungsgemäßen Ausgestaltung unschädlich, weil sie in einer Querebene der Axialkolbenmaschine wirkt, in der der Zylinder radial abgestützt ist und somit kein Kippmoment auf den Zylinder auszuüben vermag.is considered. A spherical control surface leads to a radial force component, but the radial force component is harmless in the embodiment according to the invention because it acts in a transverse plane of the axial piston machine, in which the cylinder is supported radially and thus cannot exert a tilting moment on the cylinder.

Bei der erfindungsgemäßen Ausgestaltung ist der Zylinder sowohl axial als auch radial von bedeutenden schädlichen Krafteinwirkungen befreit. Dies führt zu einer optimalen Anlage des Zylinders an der sphärischen Steuerfläche, wobei aufgrund des Gleichgewichtes der Steuerflächenkraft und der Belastungskraft sich ein wirksamer Ölfilm zwischen der Steuerfläche und dem Zylinder ausbilden kann, wodurch Reibung und Verschleiß auf ein Minimum begrenzt werden.In the embodiment according to the invention, the cylinder is freed of significant damaging forces both axially and radially. This leads to an optimal contact of the cylinder on the spherical control surface, whereby an effective oil film can form between the control surface and the cylinder due to the balance of the control surface force and the load force, whereby friction and wear are minimized.

Dabei ist zu berücksichtigen, daß sowohl die Belastungskraft als auch die Steuerflächenkraft aus mehreren Teilkräften bestehen können, z. B. nehmen auch die bei der Verschiebung der Kolben wirksamen Reibungskräfte in beiden axialen Richtungen Einfluß sowohl auf die Steuerflächenkraft als auch auf die Belastungskraft.It should be borne in mind that both the loading force and the control surface force can consist of several partial forces, e.g. B. the frictional forces acting in the displacement of the pistons in both axial directions also influence both the control surface force and the loading force.

Außerdem kann der Zylinder durch eine zentrische Federkraft, z. B. in Form einer Druckfeder, ständig gegen die Druckfläche beaufschlagt sein, wie es beim Stande der Technik gemäß DE-OS 22 50 510 der Fall ist. Die von der Feder erzeugte Teilkraft ist Teil der Belastungskraft.In addition, the cylinder by a central spring force, for. B. in the form of a compression spring, constantly applied against the pressure surface, as is the case with the prior art according to DE-OS 22 50 510. The partial force generated by the spring is part of the loading force.

Die Ausgestaltung nach Anspruch 2 ist aus zweierlei Gründen vorteilhaft. Zum einen ergibt sich aufgrund der zur Steuerfläche kegelig verjüngenden Kolbenbahn ein kleinerer Radius für die Steueröffnungen in der Steuerfläche. Infolgedessen sind aufgrund eines verhältnismäßig kleinen Druckfeldes und des kürzeren Hebelarmes die hervorgerufenen Teilkräfte der Steuerflächenkraft geringer, was kleinere Belastungszylinder ermöglicht. Zum anderen wird aufgrund dieser Ausgestaltung Bauraum für die Belastungszylinder gewonnen.The embodiment according to claim 2 is advantageous for two reasons. On the one hand, due to the piston path tapering conically to the control surface, there is a smaller radius for the control openings in the control surface. As a result, due to a relatively small pressure field and the shorter lever arm, the partial forces of the control surface force caused are lower, which enables smaller loading cylinders. On the other hand, space is gained for the loading cylinders due to this configuration.

Bei einer Ausgestaltung nach Anspruch 3 ist gewährleistet, daß die Kolben der Belastungszylinder ständig an ihrer Wirkfläche anliegen und deshalb auch der Zylinder auch im drucklosen Zustand an der Steuerfläche anliegt. Ein weiterer Vorteil der Federvorspannung für die Kolben der Belastungszylinder ist darin zu sehen, daß aufgrund des verhältnismäßig großen Drehachsenabstandes die Federkraft in den Belastungszylindern sehr wirksam ist gegen radial am Zylinder wirksame Kippmomente, die beispielsweise durch Turbulenzen in der Mediumströmung oder durch Massenkräfte hervorgerufen werden können. Als Vergleich sei hier angeführt, daß übliche axiale Federkräfte zum Zweck des Andrucks des Zylinders an die Steuerfläche im Bereich der Antriebswelle weniger wirksam sind, weil der ihnen konstruktiv vorgegebene Wirkabstand gering ist. Es ist vorteilhaft, sowohl aus Kostengründen als auch aus Gründen der Baugröße, die Ausbildung nach Anspruch 4 vorzusehen, wobei es sich empfiehlt, die Kolben der Belastungszylinder zum Zweck einer automatischer Schmierung des Gleitlagers gemäß Anspruch 5 zu durchbohren.In an embodiment according to claim 3 it is ensured that the pistons of the loading cylinder are constantly in contact with their active surface and therefore the cylinder is also in contact with the control surface even in the depressurized state. Another advantage of the spring preload for the pistons of the loading cylinders is that the spring force in the loading cylinders is very effective due to the relatively large distance between the axes of rotation against tilting moments effective radially on the cylinder, which can be caused, for example, by turbulence in the medium flow or mass forces. As a comparison, it should be mentioned here that conventional axial spring forces are less effective for the purpose of pressing the cylinder onto the control surface in the area of the drive shaft, because the effective distance that is predetermined for them is small. It is advantageous both for cost reasons and for reasons of the size to provide the design according to claim 4, it being advisable to pierce the pistons of the loading cylinders for the purpose of automatic lubrication of the plain bearing according to claim 5.

Gemäß Anspruch 6 ist jedem Kolben ein Belastungszylinder zugeordnet, wobei zwischen den zueinandergehörigen Kolbenbohrungen und Belastungszylindern eine Leitungsverbindung besteht.According to claim 6, a load cylinder is assigned to each piston, wherein there is a line connection between the associated piston bores and load cylinders.

Die Ausgestaltung nach Anspruch 7 führt zu einer Anpassung der durch die Belastungszylinder erzeugten Ausgleichskraft an den tatsächlichen Druckverlauf in den Kolbenräumen, der aufgrund konstruktiver und naturgesetzlicher Gegebenheiten gegenüber dem Zylinder in Umfangsrichtung sozusagen phasenverschoben ist.The embodiment according to claim 7 leads to an adaptation of the balancing force generated by the loading cylinder to the actual pressure profile in the piston chambers, which is due to structural and natural law conditions relative to the cylinder in the circumferential direction, so to speak, out of phase.

Nachfolgend werden vierBelow are four

Ausführungsbeispiele der Erfindung anhand einer vereinfachten Zeichnung beschrieben. Es zeigen:

  • Fig. 1 eine erfindungsgemäß ausgestaltete Axialkolbenmaschine im axialen Schnitt als erstes Ausführungsbeispiel;
  • Fig. 2 eine erfindungsgemäß ausgestaltete Axialkolbenmaschine im axialen Schnitt als zweites Ausführungsbeispiel;
  • Fig. 3 eine erfindungsgemäß ausgestaltete Axialkolbenmaschine im axialen Schnitt als drittes Ausführungsbeispiel;
  • Fig. 4 einen Schnitt durch die
    Axialkolbenmaschine nach Fig. 1 entlang der Linie IV-IV in Fig. 1, der jedoch um 90° im Uhrzeigersinn verdreht ist;
  • Fig. 5 einen der Fig. 4 entsprechenden Schnitt eines vierten Ausführungsbeispiels, der jedoch entgegen dem Uhrzeigersinn um 90° verdreht ist.
Embodiments of the invention described with reference to a simplified drawing. Show it:
  • 1 shows an axial piston machine designed according to the invention in axial section as a first exemplary embodiment;
  • 2 shows an axial piston machine designed according to the invention in axial section as a second exemplary embodiment;
  • 3 shows an axial piston machine designed according to the invention in axial section as a third exemplary embodiment;
  • Fig. 4 shows a section through the
    1 along the line IV-IV in Figure 1, but which is rotated 90 ° clockwise.
  • Fig. 5 is a section corresponding to FIG. 4 of a fourth embodiment, which is, however, rotated counterclockwise by 90 °.

Die in Fig. 1 allgemein mit 1 bezeichnete Axialkolbenmaschine, die als Pumpe und als Motor betrieben werden kann, besteht aus einem allgemein mit 2 bezeichneten Gehäuse, einer darin um eine Drehachse 3 drehbar gelagerten Antriebswelle 4, einer sogenannten Schrägscheibe 5, an der mittels Gleitschuhen 6 und einer Andruckplatte 7 auf einem Teilkreis verteilt Kolben 8 gehalten sind, einen durch die Antriebswelle 4 um die Drehachse 3 drehbaren Zylinder 9, in dem die Kolben 8 in sich axial erstreckenden Kolbenbohrungen 11 verschiebbar geführt sind und einer am Gehäuse 2 unbeweglich befestigten Steuerplatte 12, deren sphärisch konvex gewölbte Steuerfläche 13 nierenförmige Steueröffnungen 14 aufweist, die während des Drehens des Zylinders 9 mit den Kolbenbohrungen 11 in oder außer Überdeckung geraten und somit im Sinne von Ventilen den Pumpbetrieb bzw. Motorbetrieb der Axialkolbenmaschine 1 steuern.The axial piston machine, generally designated 1 in FIG. 1, which can be operated as a pump and as a motor, consists of a housing generally designated 2, a drive shaft 4, which is rotatably mounted therein about an axis of rotation 3, a so-called swash plate 5, on which by means of sliding shoes 6 and a pressure plate 7, pistons 8 are held distributed on a pitch circle, a cylinder 9 rotatable by the drive shaft 4 about the axis of rotation 3, in which the pistons 8 are displaceably guided in axially extending piston bores 11 and a control plate 12 immovably attached to the housing 2 , whose spherically convexly curved control surface 13 has kidney-shaped control openings 14 which, during the rotation of the cylinder 9, come into or out of overlap with the piston bores 11 and thus control the pumping operation or motor operation of the axial piston machine 1 in the sense of valves.

Der Antrieb der Kolben 8 erfolgt durch die Schrägscheibe 5, an der die Kolben 8 lediglich axial gehalten sind. Das heißt, während des Drehens des Zylinders 9 gleiten die Gleitschuhe 6 in Umfangsrichtung an der Schrägscheibe 5, wodurch die axiale Bewegung der Kolben 8 erzeugt wird.The pistons 8 are driven by the swash plate 5, on which the pistons 8 are only held axially. That is, while the cylinder 9 is rotating, the sliding shoes 6 slide circumferentially on the swash plate 5, whereby the axial movement of the pistons 8 is generated.

Die der Steuerfläche 13 zugewandte Stirnseite des Zylinders 9 ist entsprechend der Wölbung der Steuerfläche 13 sphärisch konkav gewölbt und liegt dichtend an der Steuerfläche 13 an.The end face of the cylinder 9 facing the control surface 13 is spherically concave in accordance with the curvature of the control surface 13 and lies sealingly against the control surface 13.

Der Zylinder 9 weist eine Bohrung 15 auf, in der er von der Antriebswelle 4 mit Spiel durchfaßt wird, die im Bereich ihrer Enden mittels Wälzlager 16 und 17 gelagert ist. Der Zylinder 9 ist lediglich an seinem der Steuerfläche 13 abgewandten Ende durch ein radial wirksames Stützlager 18 an der Antriebswelle 4 abgestützt. Zwischen der Antriebswelle 4 und dem Stützlager 18 besteht eine in Umfangsrichtung wirksame Drehmitnahmeverbindung 19 in Form einer Keilnut-Verbindung. Der Zylinder 9 ist mittels einer oder mehrerer Druckfedern 21 gegen die Steuerfläche 13 vorgespannt, die gegen die der Steuerfläche 13 abgewandte Stirnseite des Zylinders 9 wirken und an einem sphärischen Lagerteil 22 abgestützt sind, das zum einen den Zylinder 9 mit einer zylindrischen Bohrung umgreift und auf dessen äußerer Kugelfläche die Andruckplatte 7 pendelnd gleitet.The cylinder 9 has a bore 15 in which it is penetrated by the drive shaft 4 with play, which is supported in the region of its ends by means of roller bearings 16 and 17. The cylinder 9 is supported only on its end facing away from the control surface 13 by a radially effective support bearing 18 on the drive shaft 4. Between the drive shaft 4 and the support bearing 18 there is a rotary driving connection 19 in the form of a keyway connection which is effective in the circumferential direction. The cylinder 9 is biased by one or more compression springs 21 against the control surface 13, which act against the end face of the cylinder 9 facing away from the control surface 13 and are supported on a spherical bearing part 22 which, on the one hand, engages around the cylinder 9 with a cylindrical bore and on whose outer spherical surface slidably slides the pressure plate 7.

Das Stützlager 18 ist im Bereich einer mit A bezeichneten Ebene angeordnet, die gleichzeitig auch die mittlere Schwenkebene der Schrägscheibe 5 ist.The support bearing 18 is arranged in the area of a plane denoted by A, which is also the central swivel plane of the swash plate 5.

Im Betrieb der Axialkolbenmaschine 1 wirken am Zylinder 9 eine allgemein mit Fs bezeichnete Steuerflächenkraft, die senkrecht zur Steuerfläche 13 gerichtet ist und den Zylinder 9 von der Steuerfläche 13 abzuheben sucht, und eine axial gerichtete, allgemein mit FER bezeichnete resultierende Belastungskraft, die den Zylinder 9 gegen die Steuerfläche 13 beaufschlagt. Die Steuerflächenkraft Fs ergibt sich im wesentlichen als Summe der partialen Drücke über dem gesamten Druckfeld und möglichen Spaltdrücken, die sich zwischen der Steuerfläche 13 und der auf ihr gleitenden Stirnfläche 23 des Zylinders 9 aufzubauen vermögen und die den Zylinder 9 von der Steuerfläche 13 abzuheben suchen. Auf die Steuerflächenkraft Fs haben mehrere Teilkräfte Einfluß, z. B. die Reibungskräfte, die aufgrund der Verschiebung der Kolben 8 und aufgrund der Strömung an den Wänden der Kolbenbohrungen 11 in beiden axialen Richtungen wirksam sind. Aus Vereinfachungsgründen soll auf eine weitere Beschreibung dieser Teilkräfte verzichtet werden. Die resultierende Belastungskraft FER umfaßt ebenfalls mehrere Teilkräfte und insbesondere eine Belastungskraft FE, mit der auf den Umfang verteilte Belastungszylinder 24 den Zylinder 9 in Richtung auf die Steuerfläche 13 beaufschlagen. Die resultierende Belastungskraft FER umfaßt auch allgemein durch FK bezeichnete Kolbenkräfte, auf die wie schon bei der Erklärung der Steuerflächenkraft Fs nicht weiter eingegangen werden soll. Auch die von den Druckfedern 21 erzeugte, nicht näher bezeichnete Kraft nimmt Einfluß auf die resultierende Belastungskraft FER.During operation of the axial piston machine 1, a control surface force, generally designated F s , which acts perpendicular to the control surface 13 and attempts to lift the cylinder 9 from the control surface 13, acts on the cylinder 9, and an axially directed, resulting load force, generally designated F ER , which Cylinder 9 acted against the control surface 13. The control surface force F s results essentially as the sum of the partial pressures over the entire pressure field and possible gap pressures which are able to build up between the control surface 13 and the end face 23 of the cylinder 9 sliding thereon and which attempt to lift the cylinder 9 off the control surface 13 . On the control surface force F s , several partial forces have an influence, e.g. B. the frictional forces which are effective in both axial directions due to the displacement of the pistons 8 and due to the flow on the walls of the piston bores 11. For reasons of simplification, a further description of these partial forces is to be dispensed with. The resulting loading force F ER likewise comprises several partial forces and in particular a loading force F E with which loading cylinders 24 distributed over the circumference act on the cylinder 9 in the direction of the control surface 13. The resulting loading force F ER also generally includes piston forces denoted by F K , which, as in the explanation of the control surface force Fs, will not be discussed further. The force, not specified, generated by the compression springs 21 also influences the resulting loading force F ER .

Die Kolben der Belastungszylinder 24 sind mit 25 und die zugehörigen Arbeitsräume mit 26 bezeichnet. Wie Fig. 4 deutlich zeigt, ist jedem Kolben 8 ein Belastungszylinder 24 zugeordnet, wobei die Kolbenbohrungen 11 mit den zu gehörigen Arbeitsräumen 26 der Belastungszylinder 24 durch radiale Kanäle 27 verbunden sind. Die Belastungskolben 25 sind mittels eines Gleitrings 28 am Gehäuse 2 abgestützt. Sie sind zum Zweck einer automatischen Schmierung der Gleitfläche 29 bei 31 durchbohrt. Während der Gleitring 28 fest am Gehäuse 2 befestigt ist, nehmen die Belastungskolben 25 an der Drehbewegung des Zylinders 9 teil. Zur Aufnahme der Belastungszylinder 24 weist der Zylinder 9 einen Flansch 32 auf.The pistons of the loading cylinder 24 are designated 25 and the associated work spaces 26. As clearly shown in FIG. 4, a load cylinder 24 is assigned to each piston 8, the piston bores 11 being connected to the associated working spaces 26 of the load cylinders 24 by radial channels 27. The loading pistons 25 are supported on the housing 2 by means of a slide ring 28. They are pierced at 31 for the purpose of automatic lubrication of the sliding surface 29. While the slide ring 28 is fixedly attached to the housing 2, the loading pistons 25 take part in the rotary movement of the cylinder 9. The cylinder 9 has a flange 32 for receiving the loading cylinders 24.

Sowohl die Steuerflächenkraft Fs als auch die von den Belastungszylindern 24 erzeugte Belastungskraft FE sind pulsierende Kräfte. Dies ergibt sich aufgrund des Druckaufbaus bzw. -abfalls in den Kolbenbohrungen 11.Both the control surface force F s and the loading force F E generated by the loading cylinders 24 are pulsating forces. This results from the pressure build-up or drop in the piston bores 11.

Da die Steuerflächenkraft Fs nicht parallel zur Drehachse 3 gerichtet ist, ist ihre parallel zur Drehachse 3 gerichtete Steuerflächenkraftkomponente FSK geringer.Since the control surface force F s is not directed parallel to the axis of rotation 3, its control surface force component F SK directed parallel to the axis of rotation 3 is lower.

Erfindungsgemäß ist vorgesehen, daß die in axialer Richtung einander entgegengesetzt am Zylinder 9 wirkenden Kräfte im Gleichgewicht stehen. Berücksichtigt man, daß die Steuerflächenkraftkomponente FSK von der Drehachse 3 einen geringeren Abstand a als die resultierende Belastungskraft FER aufweist, deren Abstand zur Drehachse 3 mit b bezeichnet ist, dann ergibt sich im Vergleich mit der Steuerflächenkraftkomponente FSK eine verhältnismäßig geringere Größe der resultierenden Belastungskraft FER, um ein Kräftegleichgewicht herzustellen. Um dies Kräftegleichgewicht zu erreichen, sind die Arbeitsflächen (Durchmesser d) der Belastungszylinder 24 entsprechend ausgelegt.According to the invention it is provided that the forces acting in opposite directions on the cylinder 9 are in equilibrium. If one takes into account that the control surface force component F SK has a smaller distance a from the axis of rotation 3 than the resulting load force F ER , the distance of which from the axis of rotation 3 is denoted by b, then the result is a relatively smaller size in comparison with the control surface force component F SK Load force F ER to create a balance of forces. In order to achieve this balance of forces, the working surfaces (diameter d) of the loading cylinder 24 are designed accordingly.

Da die Steuerflächenkraft Fs schräg gerichtet ist, ergibt sich eine radial gerichtete Kraftkomponente FR, die den Zylinder 9 radial belastet. Um diese radiale Kraftkomponente FR unschädlich zu machen, ist erfindungsgemäß der Radius R der Steuerfläche 13 so groß bemessen, daß die Kraftlinien der Steuerflächenkraft Fs und der resultierenden Belastungskraft FER sich in einem Punkt S schneiden, der auf der Querebene A liegt, in der der Zylinder 9 radial abgestützt ist. Aufgrund dieser Ausgestaltung vermag die radiale Kraftkomponente FR kein Kippmoment auf den Zylinder 9 auszuüben.Since the control surface force F s is directed obliquely, a radially directed force component F R results which radially loads the cylinder 9. In order to render this radial force component F R harmless, according to the invention the radius R of the control surface 13 is dimensioned so large that the lines of force of the control surface force F s and the resulting loading force F ER intersect at a point S which lies on the transverse plane A in which the cylinder 9 is supported radially. Due to this configuration, the radial force component F R is unable to exert a tilting moment on the cylinder 9.

Die Ausführungsform des zweiten Ausführungsbeispiels gemäß Fig. 2 unterscheidet sich vom ersten Ausführungsbeispiel lediglich dadurch, daß die Achsen der Kolben 8 in Richtung auf die Steuerfläche 13 konvergieren. Infolgedessen werden die Kolben 8 auf einer Bahn gedreht, die sich zur Steuerfläche 13 hin kegelig verjüngt. Bei einer solchen Ausgestaltung ist im Vergleich mit dem ersten Ausführungsbeispiel die Größe des DruckfeldesThe embodiment of the second exemplary embodiment according to FIG. 2 differs from the first exemplary embodiment only in that the axes of the pistons 8 converge in the direction of the control surface 13. As a result, the pistons 8 are rotated on a path which tapers conically towards the control surface 13. In such an embodiment, the size of the pressure field is compared to the first embodiment

und damit auch die Steuerflächenkraft Fs verringert, was auch durch einen verhältnismäßig geringen, wirksamen Abstand a bedingt ist. Bei dieser Ausführungsform ist die Belastungskraft FER im Gegensatz zum ersten Ausführungsbeispiel etwas schräg gerichtet. Im Prinzip ergeben sich beim zweiten Ausführungsbeispiel gleiche Kraftverhältnisse wie beim ersten Ausführungsbeispiel.and thus also reduces the control surface force F s , which is also due to a relatively small, effective distance a. In this embodiment, the loading force F ER is directed somewhat obliquely in contrast to the first embodiment. In principle, the same force relationships as in the first exemplary embodiment result in the second exemplary embodiment.

Das dritte Ausführungsbeispiel gemäß Fig. 3 unterscheidet sich vom zweiten Ausführungsbeispiel im wesentlichen dadurch, daß keine den Zylinder 9 in Richtung auf die Steuerfläche 13 beaufschlagende Druckfedern vorgesehen sind, die gemäß Fig. 1 mit 21 bezeichnet sind. Statt dessen sind entsprechende Federn 21 in den Belastungszylindern vorgesehen, wo sie sowohl ein Abheben der Kolben 24 im drucklosen Zustand, als auch eine wirksame Anlage des Zylinders 9 an die sphärische Steuerfläche bewirken. Eine gewisse Anlagekraft ist nicht schädlich, sofern sie gering ist.The third exemplary embodiment according to FIG. 3 differs from the second exemplary embodiment essentially in that no compression springs are provided which act on the cylinder 9 in the direction of the control surface 13 and which are designated 21 in FIG. 1. Instead, corresponding springs 21 are provided in the load cylinders, where they both cause the pistons 24 to lift up in the unpressurized state and also cause the cylinder 9 to effectively rest against the spherical control surface. A certain investment power is not harmful if it is low.

Die Fig. 4 und 5 zeigen einen je wechselseitig um 90° verdrehten Querschnitt durch die Axialkolbenmaschine nach Fig. 1 entlang der Linie IV-IV bzw. in der Ebene der Verbindungskanäle 27. Dabei ist zu berücksichtigen, daß die Fig. 5 eine gegenüber der Fig. 4 abgewandelte Ausführungsform als viertes Ausführungsbeispiel zeigt. Die Steuerfläche 13 ist mit gestrichelten Linien angedeutet. Die Nierenform der ebenfalls mit gestrichelten Linien dargestellten Steueröffnungen 14 ist deutlich erkennbar.4 and 5 show a cross-section rotated by 90 ° alternately through the axial piston machine according to FIG. 1 along the line IV-IV or in the plane of the connecting channels 27. It should be taken into account that FIG. 5 is a relative to the Fig. 4 shows a modified embodiment as a fourth embodiment. The control surface 13 is indicated by dashed lines. The kidney shape of the control openings 14, also shown with dashed lines, is clearly recognizable.

Das vierte Ausführungsbeispiel gemäß Fig. 5 unterscheidet sich vom ersten Ausführungsbeispiel gemäß Fig. 4 dadurch, daß das mit Querschraffur angedeutete Druckfeld 33 der Steuerfläche 13 um einen bestimmten Winkel w gegen die Totpunktachse 34 verdreht ist. Die Belastungszylinder 24 sind in die gleiche Umfangsrichtung (siehe Drehrichtung 35) um einen Winkel w1 voreilig verdreht. Infolgedessen wirkt die Belastungskraft FE in Anpassung an den Druckaufbau bzw. -abbau in den Kolbenräumen 11 ebenfalls voreilend.The fourth exemplary embodiment according to FIG. 5 differs from the first exemplary embodiment according to FIG. 4 in that the pressure field 33 of the control surface 13 indicated with cross hatching is rotated by a certain angle w against the dead center axis 34. The loading cylinders 24 are prematurely rotated in the same circumferential direction (see direction of rotation 35) by an angle w 1 . As a result, the loading force F E also has a leading effect in adaptation to the pressure build-up or reduction in the piston chambers 11.

Claims (7)

1. An axial piston machine (1) of the inclined disc type, in particular an axial piston pump,
- having a cylinder (9) which can rotate about an axis of rotation, in which, on a pitch circle, several pistons (8) are movably guided in piston bores (11) extending substantially along the axis of rotation (3) by means of an inclined disc (5),
- the piston bores (11) opening at the face (23) of the cylinder (9) which is remote from the inclined disc (5),
- the face (23) resting against a control surface (13 in which there are arranged control openings (14), positioned on the pitch circle of the pistons (8) which, in set positions of rotation of the cylinder (9), are covered by the openings of the piston bores (11),
- wherein the piston bores (11) open at the face (23) without reduction in cross-section,
- and loading cylinders (24) being distributed on the periphery which, when the axial piston machine (1) is in operation, load the cylinder (9) against the control surface (13) for the purpose of compensating an engaging control surface force (FSK) which tries to lift the cylinder (9) from the control surface (13),
- and its working chambers are each connected to a piston bore (11) by way of connecting channels (27),
- and wherein the cylinder (9) is supported radially on the shaft by a support bearing (18), characterised in that
- the face (23) is spherically concave and the control surface (13) is correspondingly spherically convex;
-the radius (R) of the control surface (13) is such that the intersecting point (S) of the control surface force (Fs) perpendicular to the control surface (13) and of the loading force (FER) lies in a plane (A) which extends transversely to the axis of rotation (3) and which is arranged in the region of the support bearing (18) of the cylinder (9),
- and said plane (A) and the swash plane (B) of the inclined disc (5) intersect in the axis of rotation (3).
2. An axial piston machine according to claim 1, characterised in that the axes of the pistons (8) and of the piston bores (11) converge conically towards the control surface (13).
3. An axial piston machine according to claim 1 or claim 2, characterised in that in at least some of the loading cylinders (24) springs (21) are evenly distributed around the circumference which load the cylinder (9) in the direction of the control surface (13).
4. An axial piston machine according to any one of claims 1 to 3, characterised in that the loading pistons (25) of the loading cylinders (24) are supported against the housing (2) by means of a sliding ring (28).
5. An axial piston machine according to claim 4, characterised in that the loading pistons (25) are bored axially.
6. An axial piston machine according to any one of claims 1 to 5, characterised in that there is a respective loading cylinder (24) for each piston (8).
7. An axial piston machine according to any one of claims 1 to 6, characterised in that the loading cylinders (24) are offset by an angle (Wi), relative to the pistons (8) and the piston bores (11), in the direction of rotation (35).
EP85103801A 1984-04-06 1985-03-29 Axial piston machine, especially a pump of the inclined plate type Expired EP0162238B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3413059 1984-04-06
DE3413059A DE3413059C1 (en) 1984-04-06 1984-04-06 Axial piston machine, in particular pump of the swashplate or bevel axis type

Publications (2)

Publication Number Publication Date
EP0162238A1 EP0162238A1 (en) 1985-11-27
EP0162238B1 true EP0162238B1 (en) 1988-11-02

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US (1) US4602554A (en)
EP (1) EP0162238B1 (en)
JP (1) JPS60230570A (en)
DE (2) DE3413059C1 (en)

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Also Published As

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JPS60230570A (en) 1985-11-16
DE3566016D1 (en) 1988-12-08
DE3413059C1 (en) 1985-07-11
EP0162238A1 (en) 1985-11-27
US4602554A (en) 1986-07-29

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