EP0301230A2 - Axial or radial piston machine with a valve arrangement comprising a valve ring - Google Patents

Axial or radial piston machine with a valve arrangement comprising a valve ring Download PDF

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Publication number
EP0301230A2
EP0301230A2 EP88109856A EP88109856A EP0301230A2 EP 0301230 A2 EP0301230 A2 EP 0301230A2 EP 88109856 A EP88109856 A EP 88109856A EP 88109856 A EP88109856 A EP 88109856A EP 0301230 A2 EP0301230 A2 EP 0301230A2
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EP
European Patent Office
Prior art keywords
valve
ring
piston machine
piston
machine according
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Granted
Application number
EP88109856A
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German (de)
French (fr)
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EP0301230B1 (en
EP0301230A3 (en
Inventor
Manfred Lotter
Rainer Stölzer
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Hydromatik GmbH
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Hydromatik GmbH
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Publication of EP0301230A3 publication Critical patent/EP0301230A3/en
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    • 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
    • F01B3/02—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis with wobble-plate

Definitions

  • the invention relates to a piston machine according to the preamble of claim 1.
  • valve ring consists of an elastically stretchable material, on the basis of which it can at least partially lift off the through-flow channel openings forming the valve openings in order to open the passage of the outlet valve.
  • This known embodiment is not suitable for being used for high pressure because of considerable stresses on the valve ring.
  • the expandable valve ring will be damaged in its closed position under the effect of the high pressure or at least be stretched beyond its elasticity, as a result of which the function of the valve ring is very impaired, particularly in continuous operation.
  • the valve ring can even be pushed through in the area of the through-flow channel openings to be closed by the high pressure.
  • the invention has for its object to design a piston machine of the type mentioned in such a way that it is also suitable for high pressure.
  • the valve ring consists of a non-stretchable material which is suitable for being used without problems even for high pressure. Because of its tensile strength in the area of the valve openings to be sealed, it is therefore able to withstand very high pressures without the risk of being pressed into the valve openings or being pierced by high pressure.
  • the valve ring according to the invention does not function on the basis of stretching, but rather on the basis of radial displacement as a whole, as a result of which the opening cross sections required in each case result from the play of movement between the ring surface and the peripheral surface of the valve ring interacting with it.
  • valve ring is adjusted automatically based on the flow pressure, both of the outflowing and the inflowing fluid. Due to its flexibility, the valve ring is able to fit over the peripheral section that has the valve openings to be closed. In a conventional axial piston machine, this circumferential section is approximately 180 °. The other circumferential section of the valve ring lifts off from the ring surface, thereby creating the required flow channel cross section. In operation, the opening and closing functions of the valve ring are continuous, whereby it continuously lies against the ring surface in the circumferential direction and lifts again.
  • the invention is based on the fact that in the case of an existing piston engine, part of the valve openings is open during operation, while the other part of the valve openings is closed.
  • the uses Invention based on the knowledge that a non-stretchable valve ring can perform all valve functions at the same time, a seal being achieved on a circumferential section of approximately 180 ° due to the flexibility. It is not necessary to fix the valve ring in the circumferential direction.
  • the essential individual parts of the axial piston pump, generally designated 1 in FIG. 1, are a housing 4 consisting of a cup-shaped housing part 2 and a housing cover 3, a drive shaft 7 passing through the cup-shaped housing part 2 or the cavity 5 of the housing 4 along the central axis 6
  • a plurality, in the present case seven, of pistons 9 arranged on a pitch circle 8, correspondingly by means of a swash plate 11 arranged on the drive shaft 7 in a rotationally fixed manner dimensioned and assigned piston bores 12 of a cylinder block 13 arranged on the inside of the housing cover 3 are displaceable and generally designated 14 and 15 inlet and outlet valves for controlling the axial piston pump.
  • the swash plate 11 is mounted with its circumferential surface and with its end surface facing away from the cylinder block 13 in a radial and an axial slide bearing 16, 17.
  • the pistons 9 are held in contact with the slant surface 19 of the swash plate 11 by a retraction plate 18, the slant plate 11 being in contact through a ball head bearing 20 with a sleeve 21 arranged on the drive shaft 7, which - and thus also the retraction plate 18 - a spring 22 supported on the housing cover 3 is acted upon in the direction of the skew surface 19.
  • the pistons 9 have spherical piston heads with which they are mounted in an articulated but axially fixed manner in sliding shoes 23 which slide on the inclined surface 19.
  • the inlet valves 14 are formed by a channel connection running inside the piston 9 and emerging radially at a specific point on the piston jacket 24.
  • the arrangement is such that this point, designated 25, is exposed in the retracted position of the respective piston 9 to the cavity 5 of the housing 4, but is covered by the wall of the associated piston bore 12 in the advanced position of the respective piston 9.
  • the distance a of this point 25 from the edge 26 of the associated piston bore 12 in the retracted position of the piston 9 is to be adapted to the functional requirements of the axial piston pump 1 and is approximately 2 mm in the present exemplary embodiment.
  • the piston bore 12 is filled by negative pressure from the cavity 5 of the housing 4, which is filled with fluid during operation.
  • pistons 9 with a bore 27 (hollow piston) extending from their end face are used.
  • the opening to the cavity 5 is formed by at least one, preferably four radial bores 28.
  • the exhaust valves 15 have a common valve ring 31, which is arranged with radial movement play S 1 and lateral movement play S 2 in an annular groove 32, which in the present exemplary embodiment surrounds all the existing piston bores 12 and - seen radially - is arranged in the region of the inner ends of the piston bores 12 .
  • the outlet valves 15 are further formed by delivery channels 33 with valve openings 34, which exit from the piston bores 12 and open radially into an annular groove 32 and whose diameter d is smaller than the width b of the valve ring 31.
  • a further delivery channel 35 extends radially outward from the annular groove 32 from which opens into a radial connection 36 for a delivery line, not shown.
  • the cylinder block 13 protrudes by the dimension designated c into the cylindrical section 37 of the cup-shaped housing 2, an annular body 41 being inserted between the outer lateral surface 38 of the cylinder block 12 and the cylindrical inner lateral surface 39 of the section 37 (see distance B) is axially fixed at its end facing the swash plate 11 to a shoulder 42 of the housing part 2 and at its other end to a shoulder 43 of the cylinder block 13, and the ring channel 32 limited on its side facing the swash plate 11.
  • the ring channel 32 is delimited by the housing cover 3 or its flange-shaped extension. The housing cover 3 is thus centered on the annular body 41 in the cylindrical recess of the housing part 2.
  • the ring body 41 fits with a fine fit on the cylinder block 13 and in the housing part 2.
  • O-rings 40 can be provided in ring grooves between the ring body 41 and adjoining parts (housing part 2) and the housing part 2 and the housing cover 3.
  • the housing cover 3 is fastened to the housing part 2 by screws 44.
  • the fluid is sucked through an indicated suction line, which can be connected to a radial line connection 45, and a flow channel 46 adjoining the line connection 45 into the cavity 5 of the housing 4 and further into the piston bores 12 as described above.
  • the pistons 9 are fed, in which essentially half of the number of pistons 9 present, in the present exemplary embodiment seven, participates, the fluid flows out of the piston bores 12 in the direction of the flow arrows designated 47 in FIG. 2 into the annular channel 32 and further pushed laterally through the gaps 48 between the valve ring 31 and the radial walls of the ring channel 32 past the valve ring 31, the fluid passing through the delivery channel 34 to the indicated delivery line.
  • the existing valve openings 34 are each opened or closed by a radial displacement of the valve ring 31, as can best be seen in FIG. 2.
  • the valve ring 31 is due to the the flow pressure of the fluid exiting through the valve openings 34 automatically moves him into the position in which he opens the valve openings 34 discharging the pressurized fluid (left side).
  • the diametrically opposed valve openings 34 (right side) are closed at the same time, the negative pressure contained in the associated piston bores 12 and possibly the pressure on this side of the valve ring 31, the tight contact of the valve ring 31 on the annular surface containing the valve openings 34 49 of the ring channel 32 causes.
  • the valve ring 31 is able to contact the ring surface 49 of the ring channel 32 by approximately 180 °, ie to deform or bend in such a way that it consists of a flexible, preferably elastically flexible material such as metal or plastic.
  • the size of the movement s1, s2 or column depends on the throughput or delivery volume of the axial piston pump 1. The arrangement must be such that the fluid can be conveyed out of the piston bores 12 without significant throttling losses.
  • the size of the movement s1, s2 or column 48 is thus also dependent on the number of pistons 9, because with a larger number of pistons 9, the delivery volume is also larger.
  • the movement play s 1, s 2 or the column 48 can be dimensioned relatively small.
  • the size of the movement s1, s2 or gap widths depend on the throughput or delivery volume of the axial piston machine 1. With a diameter of the valve ring 31 of about 50 mm, about 0.3 to 1 mm should be aimed for. In experiments, good results were achieved with a movement clearance or a gap width of approximately 0.5 mm. This makes it clear that the Elasticity of the valve ring can be relatively low.
  • the embodiment according to the invention can also be used for piston machines with an adjustable throughput quantity, since the above-described relationship allows deviations of certain sizes.
  • valve arrangement according to the invention in contrast to the prescribed valve ring 31 as an outer ring, it is also possible to design the valve arrangement according to the invention with a valve ring as an inner ring.
  • configuration according to the invention can also be implemented on a radial piston machine (pump).

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

Abstract

An axial or radial piston machine having a plurality of pistons (9) arranged opposite one another diametrically or in the shape of a star, with a control valve arrangement (15) comprising a closed valve ring (31), which interacts with a ring surface (49) containing the valve openings, as a valve seat, is to be designed such that the machine is also suitable for high pressure. This is achieved by a radial movement play (s1) being provided between the ring surface (49) and the circumferential surface of the valve ring (31) interacting therewith, and by the valve ring (31) being flexible, but not expandable. <IMAGE>

Description

Die Erfindung bezieht sich auf einen Kolbenmaschine nach dem Oberbegriff des Anspruchs 1.The invention relates to a piston machine according to the preamble of claim 1.

Eine Radialkolbenmaschine dieser Art ist als Pumpe in der DE-OS 36 23 797 beschrieben und dargestellt. Bei der bekannten Ausgestaltung besteht der Ventilring aus einem elastisch dehnbaren Material, aufgrund dessen er wenigstens partial von den die Ventilöffnungen bildenden Durchsatzkanalmündungen abzuheben vermag, um den Durchgang des Auslaßventils freizugeben.A radial piston machine of this type is described and shown as a pump in DE-OS 36 23 797. In the known embodiment, the valve ring consists of an elastically stretchable material, on the basis of which it can at least partially lift off the through-flow channel openings forming the valve openings in order to open the passage of the outlet valve.

Diese bekannte Ausgestaltung eignet sich wegen erheb­lichen Beanspruchungen des Ventilringes nicht dazu, für den Hochdruck eingesetzt zu werden. In diesem Einsatz­fall besteht die Gefahr, daß der dehnbare Ventilring in seiner Schließposition unter der Wirkung des Hochdrucks beschädigt oder zumindest über seine Elastizität hinaus gedehnt wird, wodurch die Funktion des Ventilrings insbesondere im Dauerbetrieb sehr beeinträchtigt wird. Bei nicht ausreichender Materialfestigkeit, die sich angesichts der erforderlichen Dehnung kaum realisieren läßt, ist sogar mit einer Durchdrückung des Ventilrings im Bereich der zu verschließenden Durchsatzkanalöffnungen durch den Hochdruck zu rechnen.This known embodiment is not suitable for being used for high pressure because of considerable stresses on the valve ring. In this application, there is a risk that the expandable valve ring will be damaged in its closed position under the effect of the high pressure or at least be stretched beyond its elasticity, as a result of which the function of the valve ring is very impaired, particularly in continuous operation. In the case of insufficient material strength, which can hardly be achieved in view of the required expansion, the valve ring can even be pushed through in the area of the through-flow channel openings to be closed by the high pressure.

Der Erfindung liegt die Aufgabe zugrunde, eine Kolbenma­schine der eingangs bezeichneten Art so auszugestalten, daß sie sich auch für den Hochdruck eignet.The invention has for its object to design a piston machine of the type mentioned in such a way that it is also suitable for high pressure.

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

Bei der erfindungsgemäßen Ausgestaltung besteht der Ventilring aus einem nicht dehnbaren Material, das geeignet ist, auch für Hochdruck problemlos verwendet zu werden. Er vermag somit aufgrund seiner Zugfestigkeit im Bereich der abzudichtenden Ventilöffnungen auch sehr hohen Drücken zu widerstehen, ohne daß die Gefahr besteht, in die Ventilöffnungen eingedrückt oder vom Hochdruck durchstoßen zu werden. Im Gegensatz zur bekannten Ausgestaltung funktioniert der erfindungsgemäße Ventilring nicht aufgrund von Dehnung, sondern aufgrund von radialer Verlagerung insgesamt, durch die aufgrund des Bewegungs­spiels zwischen der Ringfläche und der mit dieser zusammen­wirkenden Umfangsfläche des Ventilrings sich die jeweils notwendigen Öffnungsquerschnitte ergeben. Dabei erfolgt die Verstellung des Ventilrings automatisch aufgrund des Strömungsdruckes, sowohl des abströmenden als auch des zufließenden Fluids. Aufgrund seiner Biegsamkeit vermag der Ventilring sich über den Umfangsabschnitt, der die zu schließenden Ventilöffnungen aufweist, anzu­legen. Bei einer üblichen Axialkolbenmaschine beträgt dieser Umfangsabschnitt in etwa 180°. Dabei hebt der andere Umfangsabschnitt des Ventilringes von der Ringfläche ab, wodurch der erforderliche Strömungskanalquerschnitt geschaffen wird. Im Betrieb sind die Öffnungs- und Schließfunktionen des Ventilrings kontinuierlich, wobei er sich in Umfangsrichtung fortlaufend an der Ringfläche anlegt und wieder abhebt.In the embodiment according to the invention, the valve ring consists of a non-stretchable material which is suitable for being used without problems even for high pressure. Because of its tensile strength in the area of the valve openings to be sealed, it is therefore able to withstand very high pressures without the risk of being pressed into the valve openings or being pierced by high pressure. In contrast to the known embodiment, the valve ring according to the invention does not function on the basis of stretching, but rather on the basis of radial displacement as a whole, as a result of which the opening cross sections required in each case result from the play of movement between the ring surface and the peripheral surface of the valve ring interacting with it. The valve ring is adjusted automatically based on the flow pressure, both of the outflowing and the inflowing fluid. Due to its flexibility, the valve ring is able to fit over the peripheral section that has the valve openings to be closed. In a conventional axial piston machine, this circumferential section is approximately 180 °. The other circumferential section of the valve ring lifts off from the ring surface, thereby creating the required flow channel cross section. In operation, the opening and closing functions of the valve ring are continuous, whereby it continuously lies against the ring surface in the circumferential direction and lifts again.

Die Erfindung geht von der Tatsache aus, daß bei einer vorliegenden Kolbenmaschine im Betrieb ein Teil der Ventilöffnungen offen ist, während der andere Teil der Ventilöffnungen geschlossen ist. Dabei nutzt die Erfindung die Erkenntnis aus, daß ein nicht dehnbarer Ventilring alle Ventilfunktionen gleichzeitig zu erfüllen vermag, wobei aufgrund der Biegsamkeit eine Abdichtung auf einem Umfangsabschnitt von etwa 180° erreicht wird. Einer Fixierung des Ventilrings in Umfangsrichtung bedarf es nicht.The invention is based on the fact that in the case of an existing piston engine, part of the valve openings is open during operation, while the other part of the valve openings is closed. The uses Invention based on the knowledge that a non-stretchable valve ring can perform all valve functions at the same time, a seal being achieved on a circumferential section of approximately 180 ° due to the flexibility. It is not necessary to fix the valve ring in the circumferential direction.

In den Unteransprüchen sind vorteilhafte Weiterbildungen der Erfindung beschrieben. Durch die Ausgestaltung nach Anspruch 2 läßt sich die Abhebefunktion des Ventil­rings verbessern. Als Werkstoff für den Ventilring eignet sich sowohl Metall als auch Kunststoff. Die in den Ansprüchen 4 bis 9 enthaltenen Merkmale sind aus baulichen Gründen von Vorteil, wobei sie eine einfache, funktionstüchtige und leistungsstarke Kolbenmaschine ergeben.Advantageous developments of the invention are described in the subclaims. The lifting function of the valve ring can be improved by the configuration according to claim 2. Both metal and plastic are suitable as the material for the valve ring. The features contained in claims 4 to 9 are advantageous for structural reasons, resulting in a simple, functional and powerful piston machine.

Nachfolgend wird die Erfindung anhand eines in einer Zeichnung dargestellten bevorzugten Ausführungsbeispiels erläutert. Es zeigt:

  • Fig. 1 eine erfindungsgemäß ausgestaltete Axialkolben­pumpe im axialen Schnitt;
  • Fig. 2 den Schnitt II-II in Fig. 1.
The invention is explained below on the basis of a preferred exemplary embodiment illustrated in a drawing. It shows:
  • 1 shows an axial piston pump designed according to the invention in axial section;
  • 2 shows the section II-II in Fig. 1st

Die wesentlichen Einzelteile der in Fig. 1 allgemein mit 1 bezeichneten Axialkolbenpumpe sind ein aus einem topfförmigen Gehäuseteil 2 und einem Gehäusedeckel 3 bestehendes Gehäuse 4, eine das topfförmige Gehäuseteil 2 bzw. den Hohlraum 5 des Gehäuses 4 längs der Mittelachse 6 durchsetzende Antriebswelle 7, eine Mehrzahl, im vorliegenden Fall sieben, auf einem Teilkreis 8 angeordnete Kolben 9, die mittels einer auf der Antriebswelle 7 drehfest angeordneten Schiefscheibe 11 in entsprechend bemessenen und zugeordneten Kolbenbohrungen 12 eines innenseitig am Gehäusedeckel 3 angeordneten Zylinderblocks 13 verschiebbar sind und allgemein mit 14 und 15 bezeich­nete Ein- und Auslaßventile zur Steuerung der Axialkolben­pumpe.The essential individual parts of the axial piston pump, generally designated 1 in FIG. 1, are a housing 4 consisting of a cup-shaped housing part 2 and a housing cover 3, a drive shaft 7 passing through the cup-shaped housing part 2 or the cavity 5 of the housing 4 along the central axis 6 A plurality, in the present case seven, of pistons 9 arranged on a pitch circle 8, correspondingly by means of a swash plate 11 arranged on the drive shaft 7 in a rotationally fixed manner dimensioned and assigned piston bores 12 of a cylinder block 13 arranged on the inside of the housing cover 3 are displaceable and generally designated 14 and 15 inlet and outlet valves for controlling the axial piston pump.

Beim vorliegenden Ausführungsbeispiel ist die Schiefscheibe 11 mit ihrer Umfangsfläche und mit ihrer dem Zylinderblock 13 abgewandten Stirnfläche in einem radialen und einem axialen Gleitlager 16, 17 gelagert. Die Kolben 9 werden durch eine Rückzugplatte 18 in Kontakt mit der Schieffläche 19 der Schiefscheibe 11 gehalten, wobei die Schiefscheibe 11 durch ein Kugelkopflager 20 mit einer auf der Antriebs­welle 7 angeordneten Hülse 21 in Kontakt steht, die - und somit auch die Rückzugplatte 18 - durch eine am Gehäusedeckel 3 abgestützte Feder 22 in Richtung auf die Schieffläche 19 beaufschlagt ist. Die Kolben 9 weisen kugelförmige Kolbenköpfe auf, mit denen sie gelenkig, jedoch axial ortsfest in an der Schieffläche 19 gleitenden Gleitschuhen 23 gelagert sind.In the present exemplary embodiment, the swash plate 11 is mounted with its circumferential surface and with its end surface facing away from the cylinder block 13 in a radial and an axial slide bearing 16, 17. The pistons 9 are held in contact with the slant surface 19 of the swash plate 11 by a retraction plate 18, the slant plate 11 being in contact through a ball head bearing 20 with a sleeve 21 arranged on the drive shaft 7, which - and thus also the retraction plate 18 - a spring 22 supported on the housing cover 3 is acted upon in the direction of the skew surface 19. The pistons 9 have spherical piston heads with which they are mounted in an articulated but axially fixed manner in sliding shoes 23 which slide on the inclined surface 19.

Beim vorliegenden Ausführungsbeispiel werden die Einlaßven­tile 14 durch eine innerhalb des Kolbens 9 verlaufende und radial an einer bestimmten Stelle des Kolbenmantels 24 austretende Kanalverbindung gebildet. Die Anordnung ist so getroffen, daß diese mit 25 bezeichnete Stelle in der zurückgezogenen Position des jeweiligen Kolbens 9 zum Hohlraum 5 des Gehäuses 4 freiliegt, jedoch in der vorgeschobenen Position des jeweiligen Kolbens 9 von der Wand der zugehörigen Kolbenbohrung 12 abgedeckt ist. Der Abstand a dieser Stelle 25 vom Rand 26 der zugehörigen Kolbenbohrung 12 in der zurückgezogenen Stellung des Kolbens 9 ist an die funktionellen Anforderun­gen der Axialkolbenpumpe 1 anzupassen und beträgt beim vorliegenden Ausführungsbeispiel etwa 2 mm. In dieser zurückgezogenen Position des Kolbens 9 erfolgt das Füllen der Kolbenbohrung 12 durch Unterdruck aus dem Hohlraum 5 des Gehäuses 4, der im Betrieb mit Fluid gefüllt ist.In the present exemplary embodiment, the inlet valves 14 are formed by a channel connection running inside the piston 9 and emerging radially at a specific point on the piston jacket 24. The arrangement is such that this point, designated 25, is exposed in the retracted position of the respective piston 9 to the cavity 5 of the housing 4, but is covered by the wall of the associated piston bore 12 in the advanced position of the respective piston 9. The distance a of this point 25 from the edge 26 of the associated piston bore 12 in the retracted position of the piston 9 is to be adapted to the functional requirements of the axial piston pump 1 and is approximately 2 mm in the present exemplary embodiment. In this retracted position of the piston 9, the piston bore 12 is filled by negative pressure from the cavity 5 of the housing 4, which is filled with fluid during operation.

Beim vorliegenden Ausführungsbeispiel werden Kolben 9 mit einer von ihrer Stirnseite ausgehenden Bohrung 27 (Hohlkolben) eingesetzt. Die Öffnung zum Hohlraum 5 hin ist durch wenigstens eine, vorzugsweise vier radiale Bohrungen 28 gebildet.In the present exemplary embodiment, pistons 9 with a bore 27 (hollow piston) extending from their end face are used. The opening to the cavity 5 is formed by at least one, preferably four radial bores 28.

Die Auslaßventile 15 weisen einen gemeinsamen Ventilring 31 auf, der mit radialem Bewegungsspiel S₁ und seitlichem Bewegungsspiel S₂ in einer Ringnut 32 angeordnet ist, die beim vorliegenden Ausführungsbeispiel alle vorhandenen Kolbenbohrungen 12 umgibt und - radial gesehen - im Bereich der inneren Enden der Kolbenbohrungen 12 angeordnet ist. Die Auslaßventile 15 werden weiter durch von den Kolbenbohrungen 12 ausgehende und radial in eine Ringnut 32 ausmündende Förderkanäle 33 mit Ventilöffnungen 34 gebildet, deren Durchmesser d geringer ist, als die Breite b des Ventilrings 31. Von der Ringnut 32 geht radial auswärts ein weiterer Förderkanal 35 aus, der in einen radialen Anschluß 36 für eine nicht dargestellte Förderleitung mündet.The exhaust valves 15 have a common valve ring 31, which is arranged with radial movement play S 1 and lateral movement play S 2 in an annular groove 32, which in the present exemplary embodiment surrounds all the existing piston bores 12 and - seen radially - is arranged in the region of the inner ends of the piston bores 12 . The outlet valves 15 are further formed by delivery channels 33 with valve openings 34, which exit from the piston bores 12 and open radially into an annular groove 32 and whose diameter d is smaller than the width b of the valve ring 31. A further delivery channel 35 extends radially outward from the annular groove 32 from which opens into a radial connection 36 for a delivery line, not shown.

Der Zylinderblock 13 ragt um das mit c bezeichnete Maß in den zylindrischen Abschnitt 37 des topfförmigen Gehäuses 2 hinein, wobei zwischen der Außenmantelfläche 38 des Zylinderblocks 12 und der zylindrischen Innenmantel­fläche 39 des Abschnitts 37 (vgl. Abstand B) ein Ringkörper 41 eingesetzt ist, der an seinem der Schiefscheibe 11 zugewandte Ende an einer Schulter 42 des Gehäuseteils 2 und an seinem anderen Ende an einer Schulter 43 des Zylinderblocks 13 axial fixiert ist, und der den Ringkanal 32 auf seiner der Schiefscheibe 11 zugewandten Seite begrenzt. Auf der anderen Seite ist der Ringkanal 32 durch den Gehäusedeckel 3 bzw. dessen flanschförmige Erstreckung begrenzt. Der Gehäusedeckel 3 ist somit mittlebar über den Ringkörper 41 in der zylindrischen Ausnehmung des Gehäuseteils 2 zentriert. Es ist zu berücksichtigen, daß der Ringkörper 41 mit einer feinen Passung auf den Zylinderblock 13 und in das Gehäuseteil 2 paßt. Zur Abdichtung des Ringkanals 32 können O-Ringe 40 in Ringnuten zwischen dem Ringkörper 41 und anliegenden Teilen (Gehäuseteil 2) sowie dem Gehäuseteil 2 und dem Gehäusedeckel 3 vorgesehen sein. Die Befestigung des Gehäusedeckels 3 am Gehäuseteil 2 erfolgt durch Schrauben 44.The cylinder block 13 protrudes by the dimension designated c into the cylindrical section 37 of the cup-shaped housing 2, an annular body 41 being inserted between the outer lateral surface 38 of the cylinder block 12 and the cylindrical inner lateral surface 39 of the section 37 (see distance B) is axially fixed at its end facing the swash plate 11 to a shoulder 42 of the housing part 2 and at its other end to a shoulder 43 of the cylinder block 13, and the ring channel 32 limited on its side facing the swash plate 11. On the other hand, the ring channel 32 is delimited by the housing cover 3 or its flange-shaped extension. The housing cover 3 is thus centered on the annular body 41 in the cylindrical recess of the housing part 2. It must be taken into account that the ring body 41 fits with a fine fit on the cylinder block 13 and in the housing part 2. To seal the ring channel 32, O-rings 40 can be provided in ring grooves between the ring body 41 and adjoining parts (housing part 2) and the housing part 2 and the housing cover 3. The housing cover 3 is fastened to the housing part 2 by screws 44.

Im Betrieb der Axialkolbenpumpe 1 wird das Fluid durch eine andeutungsweise dargestellte, an einem radialen Leitungsanschluß 45 anschließbare Saugleitung und einen sich an den Leitungsanschluß 45 anschließenden Strömungs­kanal 46 in den Hohlraum 5 des Gehäuses 4 und weiter wie vorbeschrieben in die Kolbenbohrungen 12 gesaugt. Beim Vorschub der Kolben 9, an dem jeweils im wesentlichen die Hälfte der Anzahl der vorhandenen, beim vorliegenden Ausführungsbeispiel sieben Kolben 9 teilnimmt, wird das Fluid aus den Kolbenbohrungen 12 in Richtung der in Fig. 2 mit 47 bezeichneten Strömungspfeile in den Ringkanal 32 und weiter seitlich durch die zwischen dem Ventilring 31 und den radialen Wänden des Ringkanals 32 vorhandenen Spalte 48 am Ventilring 31 vorbeigedrückt, wobei das Fluid durch den Förderkanal 34 zur angedeuteten Förderleitung gelangt.In the operation of the axial piston pump 1, the fluid is sucked through an indicated suction line, which can be connected to a radial line connection 45, and a flow channel 46 adjoining the line connection 45 into the cavity 5 of the housing 4 and further into the piston bores 12 as described above. When the pistons 9 are fed, in which essentially half of the number of pistons 9 present, in the present exemplary embodiment seven, participates, the fluid flows out of the piston bores 12 in the direction of the flow arrows designated 47 in FIG. 2 into the annular channel 32 and further pushed laterally through the gaps 48 between the valve ring 31 and the radial walls of the ring channel 32 past the valve ring 31, the fluid passing through the delivery channel 34 to the indicated delivery line.

Die vorhandenen Ventilöffnungen 34 werden jeweils durch eine radiale Verlagerung des Ventilrings 31 geöffnet oder geschlossen, wie es am besten aus Fig. 2 ersichtlich ist. Dabei wird der Ventilring 31 aufgrund des auf ihn wirkenden Strömungsdrucks des durch die Ventilöffnun­gen 34 austretenden Fluids automatisch in die Lage bewegt, in der er die unter Druck stehendes Fluid auslas­senden Ventilöffnungen 34 öffnet (linke Seite). Die diametral entgegengesetzt angeordneten Ventilöffnungen 34 (rechte Seite) werden dabei gleichzeitig geschlossen, wobei der in den zugehörigen Kolbenbohrungen 12 enthaltene Unterdruck und ggf. der auf dieser Seite auf den Ventil­ring 31 lastende Druck die dichte Anlage des Ventilrings 31 an der die Ventilöffnungen 34 enthaltenden Ringfläche 49 des Ringkanals 32 bewirkt. Der Ventilring 31 ist in der Lage, sich um ca. 180° an die Ringfläche 49 des Ringkanals 32 anzulegen, d.h. so zu verformen bzw. zu biegen, da er aus einem biegsamen, vorzugsweise elastisch biegsamen Material wie Metall oder Kunststoff besteht.The existing valve openings 34 are each opened or closed by a radial displacement of the valve ring 31, as can best be seen in FIG. 2. The valve ring 31 is due to the the flow pressure of the fluid exiting through the valve openings 34 automatically moves him into the position in which he opens the valve openings 34 discharging the pressurized fluid (left side). The diametrically opposed valve openings 34 (right side) are closed at the same time, the negative pressure contained in the associated piston bores 12 and possibly the pressure on this side of the valve ring 31, the tight contact of the valve ring 31 on the annular surface containing the valve openings 34 49 of the ring channel 32 causes. The valve ring 31 is able to contact the ring surface 49 of the ring channel 32 by approximately 180 °, ie to deform or bend in such a way that it consists of a flexible, preferably elastically flexible material such as metal or plastic.

Die Größe der Bewegungsspiele s₁, s₂ bzw. Spalte ist abhängig vom Durchsatz- bzw. Fördervolumen der Axialkolben­pumpe 1. Die Anordnung ist so zu treffen, daß das Fluid ohne wesentliche Drosselverluste aus den Kolbenbohrungen 12 herausgefördert werden kann. Die Größe des Bewegungs­spiels s₁, s₂ bzw. der Spalte 48 ist somit auch abhängig von der Anzahl der Kolben 9, denn bei einer größeren Anzahl von Kolben 9 ist auch das Fördervolumen größer. Dagegen können beim Vorhandensein einer geringen Anzahl Kolben, d.h., einem verhältnismäßig geringem Fördervolumen, die Bewegungsspiele s₁, s₂ bzw. die Spalte 48 verhältnis­mäßig klein bemessen werden.The size of the movement s₁, s₂ or column depends on the throughput or delivery volume of the axial piston pump 1. The arrangement must be such that the fluid can be conveyed out of the piston bores 12 without significant throttling losses. The size of the movement s₁, s₂ or column 48 is thus also dependent on the number of pistons 9, because with a larger number of pistons 9, the delivery volume is also larger. On the other hand, if there is a small number of pistons, i.e. a relatively small delivery volume, the movement play s 1, s 2 or the column 48 can be dimensioned relatively small.

Die Größe der Bewegungsspiele s₁, s₂ bzw. Spaltweiten sind abhängig vom Durchsatz bzw. Fördervolumen der Axialkolbenmaschine 1. Bei einem Durchmesser des Ventil­rings 31 von etwa 50 mm sollten etwa 0,3 bis 1 mm ange­strebt werden. Bei Versuchen wurden gute Ergebnisse bei einem Bewegunngsspiel bzw. einer Spaltweite von etwa 0,5 mm erzielt. Hierdurch wird deutlich, daß die Elastizität des Ventilringes verhältnismäßig gering sein kann.The size of the movement s₁, s₂ or gap widths depend on the throughput or delivery volume of the axial piston machine 1. With a diameter of the valve ring 31 of about 50 mm, about 0.3 to 1 mm should be aimed for. In experiments, good results were achieved with a movement clearance or a gap width of approximately 0.5 mm. This makes it clear that the Elasticity of the valve ring can be relatively low.

Trotz der vorbeschriebenen Beziehung zwischen der Größe der Spalte 48 und dem Durchsatzvolumen ist die erfindungs­gemäße Ausgestaltung auch für Kolbenmaschinen mit verstell­barer Durchsatzmenge einsetzbar, da die vorbeschriebene Beziehung Abweichungen bestimmter Größen erlaubt.Despite the above-described relationship between the size of the column 48 and the throughput volume, the embodiment according to the invention can also be used for piston machines with an adjustable throughput quantity, since the above-described relationship allows deviations of certain sizes.

Im Rahmen der Erfindung ist es im Gegensatz zum vorb­schriebenen Ventilring 31 als Außenring auch möglich, die erfindungsgemäße Ventilanordnung mit einem Ventilring als Innenring auszuführen. Außerdem ist erfindungsgemäße Ausgestaltung auch an einer Radialkolbenmaschine (Pumpe) zu verwirklichen.In the context of the invention, in contrast to the prescribed valve ring 31 as an outer ring, it is also possible to design the valve arrangement according to the invention with a valve ring as an inner ring. In addition, the configuration according to the invention can also be implemented on a radial piston machine (pump).

Claims (9)

1. Axial- oder Radialkolbenmaschine mit mehreren, einander diametral oder sternförmig gegenüberliegenden Kolben, mit einer Steuerventilanordnung mit einem geschlossenen Ventilring, der mit einer die Ventilöffnungen enthalten­den Ringfläche als Ventilsitz zusammenwirkt,
dadurch gekennzeichnet,
daß ein radiales Bewegungsspiel (s₁) zwischen der Ringfläche (49) und der mit dieser zusammenwirkenden Umfangsfläche des Ventilrings (31) vorgesehen ist und der Ventilring (31) nicht dehnbar, jedoch biegsam ist.1. axial or radial piston machine with a plurality of pistons diametrically or star-shaped opposite one another, with a control valve arrangement with a closed valve ring, which cooperates with an annular surface containing the valve openings as a valve seat,
characterized,
that a radial movement (s₁) between the annular surface (49) and the cooperating with this peripheral surface of the valve ring (31) is provided and the valve ring (31) is not stretchable, but flexible. 2. Kolbenmaschine nach Anspruch 1,
dadurch gekennzeichnet,
daß der Ventilring (31) elastisch biegsam ist.2. Piston machine according to claim 1,
characterized,
that the valve ring (31) is elastically flexible. 3. Kolbenmaschine nach Anspruch 1 oder 2,
dadurch gekennzeichnet,
daß der Ventilring (31) aus Metall, insbesondere Stahl, oder Kunststoff besteht.3. Piston machine according to claim 1 or 2,
characterized,
that the valve ring (31) consists of metal, in particular steel, or plastic. 4. Kolbenmaschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet,
daß der Ringkanal (32) im Bereich der inneren Enden der Kolbenbohrungen (12), vorzugsweise radial außen von den Kolbenbohrungen (12), angeordnet ist.4. Piston machine according to one of claims 1 to 3, characterized in
that the annular channel (32) is arranged in the region of the inner ends of the piston bores (12), preferably radially outside of the piston bores (12). 5. Kolbenmaschine nach einem der Ansprüch 1 bis 4, dadurch gekennzeichnet,
daß bei einer Axialkolbenmaschine der Ringkanal (32) zwischen einem die Kolbenbohrungen (12) aufweisen­den, gehäusefesten Zylinderblock (13) und einer letzteren umgebenden Wand (37) des Gehäuses (4) angeordnet ist.5. Piston machine according to one of claims 1 to 4, characterized in
that in an axial piston machine the annular channel (32) is arranged between a cylinder block (13) which has the piston bores (12) and is fixed to the housing and a wall (37) of the housing (4) surrounding the latter. 6. Kolbenmaschine nach Anspruch 5,
dadurch gekennzeichnet,
daß zwischen der Außenmantelfläche (38) des Zylinder­blocks (13) und der Wand (37) ein den Ringkanal (32) axial begrenzender Ringkörper (41) eingesetzt ist.6. Piston machine according to claim 5,
characterized,
that between the outer circumferential surface (38) of the cylinder block (13) and the wall (37) an annular body (41) axially delimiting an annular body (41) is inserted. 7. Kolbenmaschine nach Ansprunch 6,
dadurch gekennzeichnet,
daß der Ringkörper (41) zwischen einer Schulter (42) an der Wand (37) des Gehäuses (4) und einer Schulter (43) am Zylinderblock (13) axial fixiert ist.7. piston machine according to claim 6,
characterized,
that the ring body (41) between a shoulder (42) on the wall (37) of the housing (4) and a shoulder (43) on the cylinder block (13) is axially fixed. 8. Kolbenmaschine nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet,
daß der Zylinderblock (13) innenseitig an einem flanschförmigen, den Ringkanal (32) axial begrenzenden Gehäusedeckel (3) angeordnet ist, vorzugsweise ein­stückig von diesem ausgeht.8. Piston machine according to one of claims 5 to 7, characterized in that
that the cylinder block (13) is arranged on the inside on a flange-shaped housing cover (3) which axially delimits the annular channel (32), preferably starting in one piece therefrom. 9. Kolbenmaschine nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet,
daß vom Ringkanal (32) ein radialer Förderkanal (46) zu einem vorzugsweise radialen Leitungsanschluß (36) führt.9. Piston machine according to one of claims 1 to 8, characterized in
that a radial delivery channel (46) leads from the ring channel (32) to a preferably radial line connection (36).
EP88109856A 1987-07-28 1988-06-21 Axial or radial piston machine with a valve arrangement comprising a valve ring Expired - Lifetime EP0301230B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873724967 DE3724967A1 (en) 1987-07-28 1987-07-28 AXIAL OR RADIAL PISTON MACHINE WITH A VALVE RING CONTROL VALVE ARRANGEMENT
DE3724967 1987-07-28

Publications (3)

Publication Number Publication Date
EP0301230A2 true EP0301230A2 (en) 1989-02-01
EP0301230A3 EP0301230A3 (en) 1989-09-06
EP0301230B1 EP0301230B1 (en) 1991-09-25

Family

ID=6332528

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88109856A Expired - Lifetime EP0301230B1 (en) 1987-07-28 1988-06-21 Axial or radial piston machine with a valve arrangement comprising a valve ring

Country Status (2)

Country Link
EP (1) EP0301230B1 (en)
DE (2) DE3724967A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3841382C1 (en) * 1988-12-08 1990-03-15 Hydromatik Gmbh, 7915 Elchingen, De
DE4238376A1 (en) * 1992-11-13 1993-12-02 Bosch Gmbh Robert Radial piston pump with elastic valve ring - uses fluid pressure from pistons to rotate valve ring and so distribute wear uniformly
DE19740436A1 (en) * 1997-09-15 1999-03-18 Schaeffler Waelzlager Ohg Swashplate bearing for plunger pump
DE102005060957B4 (en) * 2005-12-20 2012-08-23 Industriehansa Consulting & Engineering Gmbh High pressure pump with several pistons per cylinder

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB541295A (en) * 1940-02-09 1941-11-20 Browett Lindley 1931 Ltd J Improvements in and relating to air compressors
FR2193152A1 (en) * 1972-07-19 1974-02-15 Bendix Westinghouse Ltd
DE3623797A1 (en) * 1985-07-24 1987-03-19 Barmag Barmer Maschf Radial piston pump

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB541295A (en) * 1940-02-09 1941-11-20 Browett Lindley 1931 Ltd J Improvements in and relating to air compressors
FR2193152A1 (en) * 1972-07-19 1974-02-15 Bendix Westinghouse Ltd
DE3623797A1 (en) * 1985-07-24 1987-03-19 Barmag Barmer Maschf Radial piston pump

Also Published As

Publication number Publication date
EP0301230B1 (en) 1991-09-25
EP0301230A3 (en) 1989-09-06
DE3865140D1 (en) 1991-10-31
DE3724967A1 (en) 1989-02-09

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