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EP0044070B1 - Axial piston pump with two delivery streams - Google Patents

Axial piston pump with two delivery streams Download PDF

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Publication number
EP0044070B1
EP0044070B1 EP81105478A EP81105478A EP0044070B1 EP 0044070 B1 EP0044070 B1 EP 0044070B1 EP 81105478 A EP81105478 A EP 81105478A EP 81105478 A EP81105478 A EP 81105478A EP 0044070 B1 EP0044070 B1 EP 0044070B1
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EP
European Patent Office
Prior art keywords
pitch circle
circle diameter
tilting disc
pistons
cylindrical drum
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP81105478A
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German (de)
French (fr)
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EP0044070A1 (en
Inventor
Franz Forster
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Linde GmbH
Original Assignee
Linde GmbH
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Filing date
Publication date
Application filed by Linde GmbH filed Critical Linde GmbH
Publication of EP0044070A1 publication Critical patent/EP0044070A1/en
Application granted granted Critical
Publication of EP0044070B1 publication Critical patent/EP0044070B1/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/22—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 having two or more sets of cylinders or pistons

Definitions

  • the invention relates to an axial piston pump for generating two flow rates, the size of which can be set independently of one another, with a rotating cylinder drum connected to a shaft, in which cylinder bores are arranged on two different pitch circle diameters, all of which open into the same end face of the cylinder drum, one in each cylinder bore Piston is displaceable and the pistons in the cylinders arranged on a smaller pitch circle diameter are supported against an adjustable swash plate formed on a swash plate body and the pistons in the cylinders arranged on a larger pitch circle diameter are supported against a second adjustable swash plate formed on a second swash plate body, whereby on the a control rotary valve is formed on the end face of the cylinder drum from which the pistons emerge, on the opposite end face of the cylinder drum.
  • a swash plate which are supported on a swash plate body designed as a circumferential ring, this ring being supported via a roller bearing against a swivel body which, on the one hand, is arranged against a roller-shaped one arranged outside the axis of rotation Support body is supported and on the other hand is supported against an adjusting device which is axially displaceable so that the inclination of the swash plate body relative to the axis of rotation can be adjusted.
  • the pistons which are arranged on a larger pitch circle diameter, are supported against a swash plate which is formed on an annular swash plate body, which in turn is designed as a circumferential ring and is mounted in a swivel body by means of a roller bearing, which in turn is eccentric to the axis of rotation against a roller-shaped body is supported on the other side of the axis of rotation as the support body arranged first and is also supported against an axially displaceable adjusting member (FR-A-1 340 850).
  • a swash plate which is formed on an annular swash plate body, which in turn is designed as a circumferential ring and is mounted in a swivel body by means of a roller bearing, which in turn is eccentric to the axis of rotation against a roller-shaped body is supported on the other side of the axis of rotation as the support body arranged first and is also supported against an axially displaceable adjusting member (FR-A-1 340 850).
  • This type of support for the swashplate body requires a large installation space relative to the forces that can be absorbed, so that for a given installation space only relatively small forces can be absorbed, that is to say either one can only work with a low working pressure or the pistons have a small diameter must have, and moreover, this embodiment allows only small angles of inclination for the swash plate body.
  • the known pump therefore requires a relatively large amount of space.
  • the present invention has for its object to provide an axial piston machine of the type mentioned, which can be manufactured with as few components and thus low construction costs and which also has relatively small dimensions in terms of performance and requires a correspondingly small installation space.
  • the swash plate body on which the swash plate is formed against which the pistons arranged on a smaller pitch circle diameter are supported, has a spherical cap-shaped surface on its side facing away from the swash plate and with this spherical cap-shaped surface in a spherical cap-shaped recess Swashplate body is mounted on which the swashplate is formed, against which the pistons arranged on a larger pitch circle diameter are supported.
  • This spherical cap-shaped surface and spherical cap-shaped counter surface can absorb large piston forces.
  • this configuration is the smallest spatial shape, which on the one hand enables a sufficient swash plate surface for supporting the pistons arranged on a smaller pitch circle diameter, the pitch circle diameter of the pistons arranged on a larger pitch circle diameter also being as small as possible, that is to say that the two pitch circle diameters are as tight should lie next to each other, as is possible with regard to the strength of the cylinders on the one hand and the space required for the piston supports on the other.
  • the spherical bearing surface enables the adjustment device for the pivoting of the swash plate body associated with the piston arranged on a smaller pitch circle diameter to be designed in such a way that this adjustment device additionally swivels this swash plate body a small amount about a second, to the first pivot axis and the axis of rotation vertical axis of the cylinder drum can be effected.
  • Such a small, arbitrarily brought about additional pivoting about the second pivot axis makes it possible to achieve a small pre-compression or pre-expansion while smoothing over the separating webs while keeping the separating webs in the control rotary valve in the same position and thus avoiding them operating noise.
  • a connecting device is provided, by means of which the swash plate bodies, which can be adjusted independently of one another during operation, can be arbitrarily connected to one another for the purpose of common adjustment during certain operating states. That is, in operating states in which it is desired that the flow rates of both pumps are changed to the same extent, the connection is established by this connecting device, this connection being releasable, so that in other operating states the goal is two independent flow rates to generate can be tracked.
  • the swash plate body assigned to the piston arranged on a smaller pitch circle diameter is in operative connection with a swash plate body which extends through a recess of the swash plate body assigned to the piston arranged on a larger pitch circle diameter, that is to say the adjustment of the one arranged on the smaller pitch circle diameter
  • Piston-associated swash plate body is not provided by a device that acts parallel to the axis of rotation, but by a device that extends through the outer swash plate body.
  • both swashplate bodies have a central recess through which the shaft connected to the cylinder drum projects to a free connection.
  • control base 2 and the cradle bearing part 3 are attached to the middle part of the housing. These parts are connected to each other by anchor bolts, not shown in the drawing.
  • the cylinder drum 4 is mounted in the middle part 1 of the housing by means of a roller bearing 55. With its end face 5, the cylinder drum 4 bears against a control plate 6, which in turn is rotatably mounted on the control base part 2.
  • the cylinder drum 4 has a longitudinal bore 7 which, in the part on the left in the drawing, is provided with an internal toothing 8 which engages in the toothing of a drive shaft which in turn by means of a bearing 10 (which is preferably designed as a pair of roller bearings) in the control floor 2 is stored.
  • the cover 12 serves to secure the bearing 10 and carries the seal 11.
  • a pin 13 is provided coaxially to the shaft 9 and has a collar 14 and a ball head 15.
  • a plate spring assembly 16 is supported against the collar 14, which is supported on the other hand against the cylinder drum 4.
  • the ball head 15 lies in a corresponding recess in the pressure plate 17, which has bores through which the sliding shoes 18 of the pistons 19, which are arranged with a small pitch circle diameter, protrude.
  • the sliding shoes 18 have a base part 20 against which the pressure plate 17 presses.
  • the pistons 19, which are arranged on a smaller pitch circle diameter, are displaceable in cylinder bores 21, each cylinder bore 21 being provided with an orifice channel 22 which opens into the end face 5 of the cylinder drum 4, specifically in relation to an at least approximately semicircular channel 23 in the control plate 6, which is located in continues a channel 24 in the control floor 2, the channel 24 leading to a connection, not shown in the drawing, lying next to the plane of the drawing.
  • the pistons 25 are arranged on a larger pitch circle diameter than the pistons 19, each of the pistons 25 being displaceable in a cylinder bore 26 which has an orifice channel 27, the orifice channels 27 being opposite an approximately semicircular channel 28 in the control plate 6, the channel 28 connects to a channel 29 in the control floor part 2, which leads to a connecting flange 30 for a delivery pressure line, not shown in the drawing.
  • Each piston 25 is supported against a slide shoe 31, the base part 32 of which is pressed against the swash plate 34 by a hold-down ring 33, the hold-down ring 33 being held by a pressure ring 35 which is screwed against the swash plate body 36.
  • the swash plate 34 assigned to the piston 25 arranged on a larger pitch circle diameter is thus formed on the swash plate body 36.
  • the pistons 19, which are arranged on a smaller pitch circle diameter are supported by means of their sliding shoes 18 against the swash plate 37, which is formed on the swash plate body 38 and has a spherical cap-shaped surface 39 on its rear side, which rests in a hollow spherical surface of the swash plate body 36.
  • the swash plate body 36 has a semi-cylindrical surface 40 on a rear side, which rests in a hollow cylindrical surface of the cradle bearing part 3.
  • the swashplate body 36 has a recess 41 through which an adjusting pin 42 extends, which is provided with a ball head 43 which is guided in a bore 64 in the swashplate body 38.
  • the adjusting pin 42 is on the other hand fastened in the adjusting piston 44, which is displaceable in the adjusting cylinder 45, which is formed in a corresponding extension of the cradle bearing part 3 and is closed on both sides by a cover 46, through which the hydraulic fluid lines, not shown in the drawing, pass, by means of which the actuating piston 44 can be acted upon arbitrarily with pressure medium.
  • a further extension is formed on the cradle bearing part 3, in which an actuating cylinder 47 is arranged, in which an actuating piston 48 is displaceable is.
  • the actuating cylinder 47 is also closed by two covers 46.
  • a setting pin 49 is fastened in the adjusting piston 48 and engages with its spherical head part 50 in a bore 51 of the swash plate body 36.
  • a suction channel 52 is provided in the control floor part 2, which opens into a wide opening 53 of the control plate 6, the opening 53 extending in the radial direction so far that it both before the Mouth channels 27 and in front of the mouth channels 22. In the circumferential direction, the opening 53 extends just as far as the approximately semicircular channels 23 and 28 on the other side.
  • two approximately semicircular channels can also be formed in front of the mouth of the suction channel 52, which channels correspond to the channels 23 and 28, the side of the control plate 6 facing the suction channel 52 being designed to be streamlined.
  • the control floor part 2 is designed symmetrically on both sides, that is, instead of the suction channel 52 and the opening 53, two separate channels are formed in the control floor part 2 and correspondingly two approximately semicircular channels corresponding to the channels 23 and 28 in the control plate 6 , so that the pump is designed for two closed circuits.
  • control base part 2 is shown rotated by 90 ° about the axis of the shaft 9, because in the cutting plane, which is perpendicular to the swivel axis of the swash plate bodies 36 and 38, the separating webs lie in the control plate 6, that is to say no openings in the The drawing would be recognizable if the cut were placed through it

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

Description

Die Erfindung betrifft eine Axialkolbenpumpe zum Erzeugen von zwei Förderströmen, deren Größe voneinander unabhängig einstellbar ist, mit einer Welle verbundenen umlaufenden Zylindertrommel, in der auf zwei unterschiedlichen Teilkreisdurchmessern Zylinderbohrungen angeordnet sind, die alle in der gleichen Stirnfläche der Zylindertrommel münden, wobei in jeder Zylinderbohrung ein Kolben verschiebbar ist und die Kolben in den auf kleinerem Teilkreisdurchmesser angeordneten Zylindern gegen eine an einem Schrägscheibenkörper gebildete einstellbare Schrägscheibe abgestützt sind und die Kolben in den auf größerem Teilkreisdurchmesser angeordneten Zylindern gegen eine zweite, an einem zweiten Schrägscheibenkörper gebildete einstellbare Schrägscheibe abgestützt sind, wobei auf der der Stirnseite der Zylindertrommel, aus der die Kolben austreten, entgegengesetzten Stirnfläche der Zylindertrommel ein Steuerdrehschieber gebildet ist.The invention relates to an axial piston pump for generating two flow rates, the size of which can be set independently of one another, with a rotating cylinder drum connected to a shaft, in which cylinder bores are arranged on two different pitch circle diameters, all of which open into the same end face of the cylinder drum, one in each cylinder bore Piston is displaceable and the pistons in the cylinders arranged on a smaller pitch circle diameter are supported against an adjustable swash plate formed on a swash plate body and the pistons in the cylinders arranged on a larger pitch circle diameter are supported against a second adjustable swash plate formed on a second swash plate body, whereby on the a control rotary valve is formed on the end face of the cylinder drum from which the pistons emerge, on the opposite end face of the cylinder drum.

Bei einer bekannten Axialkolbenpumpe dieser Art sind die auf kleinerem Teilkreisdurchmesser angeordneten Kolben gegen eine Schrägscheibe abgestützt, die an einem als umlaufender Ring ausgestalteten Schrägscheibenkörper abgestützt sind, wobei dieser Ring über ein Wälzlager gegen einen Schwenkkörper abgestützt ist, der einerseits gegen einen außerhalb der Drehachse angeordneten walzenförmigen Stützkörper abgestützt ist und andererseits gegen eine Einstelleinrichtung abgestützt ist, die axial verschiebbar ist, so daß die Neigung des Schrägscheibenkörpers gegenüber der Drehachse eingestellt werden kann. In ähnlicher Weise sind die auf größerem Teilkreisdurchmesser angeordneten Kolben gegen eine Schrägscheibe abgestützt, die an einem ringförmigen Schrägscheibenkörper gebildet ist, der seinerseits als umlaufender Ring ausgestaltet ist und mittels eines Wälzlagers in einem Verschwenkkörper gelagert ist, der seinerseits einerseits gegen einen Walzenförmigen, exzentrisch zur Drehachse auf der anderen Seite der Drehachse wie der erstgenannte Stützkörper angeordneten Stützkörper abgestützt ist und darüberhinaus gegen ein axial verschiebbares Einstellorgan abgestützt ist (FR-A-1 340 850). Diese Art der Abstützung der Schrägscheibenkörper erfordert relativ zu den Kräften, die aufgenommen werden können, einen großen Bauraum, so daß bei gegebenem Bauraum nur relativ kleine Kräfte aufgenommen werden können, das heißt, entweder nur mit geringem Arbeitsdruck gearbeitet werden kann oder die Kolben geringen Durchmesser haben müssen, und zudem läßt diese Ausgestaltungsform nur geringe Neigungswinkel für den Schrägscheibenkörper zu. Bezogen auf die Leistung hat die bekannte Pumpe somit einen relativ großen Raumbedarf.In a known axial piston pump of this type, the pistons arranged on a smaller pitch circle diameter are supported against a swash plate, which are supported on a swash plate body designed as a circumferential ring, this ring being supported via a roller bearing against a swivel body which, on the one hand, is arranged against a roller-shaped one arranged outside the axis of rotation Support body is supported and on the other hand is supported against an adjusting device which is axially displaceable so that the inclination of the swash plate body relative to the axis of rotation can be adjusted. Similarly, the pistons, which are arranged on a larger pitch circle diameter, are supported against a swash plate which is formed on an annular swash plate body, which in turn is designed as a circumferential ring and is mounted in a swivel body by means of a roller bearing, which in turn is eccentric to the axis of rotation against a roller-shaped body is supported on the other side of the axis of rotation as the support body arranged first and is also supported against an axially displaceable adjusting member (FR-A-1 340 850). This type of support for the swashplate body requires a large installation space relative to the forces that can be absorbed, so that for a given installation space only relatively small forces can be absorbed, that is to say either one can only work with a low working pressure or the pistons have a small diameter must have, and moreover, this embodiment allows only small angles of inclination for the swash plate body. In terms of performance, the known pump therefore requires a relatively large amount of space.

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, eine Axialkolbenmaschine der eingangs genannten Gattung zu schaffen, die mit möglichst wenig Bauteilen und somit geringem Bauaufwand hergestellt werden kann und die zudem bezogen auf die Leistung relativ kleine Abmessungen aufweist und einen entsprechend kleinen Einbauraum erfordert.The present invention has for its object to provide an axial piston machine of the type mentioned, which can be manufactured with as few components and thus low construction costs and which also has relatively small dimensions in terms of performance and requires a correspondingly small installation space.

Diese Aufgabe wird gemäß der Erfindung dadurch gelöst, daß der Schrägscheibenkörper, an dem die Schrägscheibe gebildet ist gegen die die auf kleinerem Teilkreisdurchmesser angeordneten Kolben abgestützt sind, auf seiner der Schrägscheibe abgewandten Seite eine kugelkappenförmige Fläche aufweist und mit dieser kugelkappenförmigen Fläche in einer kugelkalottenförmigen Ausnehmung des Schrägscheibenkörpers gelagert ist, an dem die Schrägscheibe gebildet ist, gegen die die auf größerem Teilkreisdurchmesser angeordneten Kolben abgestützt sind. Diese kugelkappenförmige Fläche und kugelkalottenförmige Gegenfläche vermag große Kolbenkräfte aufzunehmen. Darüberhinaus ist diese Ausgestaltung die kleinste Raumform, die einerseits eine hinreichende Schrägscheibenfläche für die Abstützung der auf kleinerem Teilkreisdurchmesser angeordneten Kolben ermöglicht, wobei der Teilkreisdurchmesser der auf größerem Teilkreisdurchmesser angeordneten Kolben ebenfalls so gering wie möglich sein soll, das heißt, daß die beiden Teilkreisdurchmesser so dicht beieinander liegen sollen, wie mit Rücksicht auf einerseits die Festigkeit der Zylinder und andererseits auf den erforderlichen Raum der Kolbenabstützungen möglich ist. Es ist zwar bereits bekannt, bei einer Triebflanschmaschine die Rückseite des Lagers des Triebflansches kugelkappenförmig auszugestalten und in einem kugelkalottenförmigen Teil des Schwenkgehäuses zu lagern (DE-C-971 352). Hierbei ist jedoch die Zielsetzung, günstige Möglichkeiten für die Schwenkbarkeit des Gehäuses gegenüber der Triebflanschwelle zu schaffen. Auch ist es bereits bekannt, einen Schrägscheibenkörper mit einem Ansatz mit kugelzonenförmigen Umfang zur Lagerung zu versehen. (DE-A-16 25 073).This object is achieved according to the invention in that the swash plate body, on which the swash plate is formed against which the pistons arranged on a smaller pitch circle diameter are supported, has a spherical cap-shaped surface on its side facing away from the swash plate and with this spherical cap-shaped surface in a spherical cap-shaped recess Swashplate body is mounted on which the swashplate is formed, against which the pistons arranged on a larger pitch circle diameter are supported. This spherical cap-shaped surface and spherical cap-shaped counter surface can absorb large piston forces. In addition, this configuration is the smallest spatial shape, which on the one hand enables a sufficient swash plate surface for supporting the pistons arranged on a smaller pitch circle diameter, the pitch circle diameter of the pistons arranged on a larger pitch circle diameter also being as small as possible, that is to say that the two pitch circle diameters are as tight should lie next to each other, as is possible with regard to the strength of the cylinders on the one hand and the space required for the piston supports on the other. It is already known to design the rear of the bearing of the drive flange in the form of a spherical cap in a drive flange machine and to store it in a spherical cap-shaped part of the swivel housing (DE-C-971 352). However, the goal here is to create favorable possibilities for the pivoting of the housing relative to the drive flange shaft. It is also already known to provide a swashplate body with an attachment with a spherical zone-shaped circumference for storage. (DE-A-16 25 073).

Darüberhinaus ermöglicht die kugelförmige Lagerfläche, gemäß einem weiteren Schritt der Erfindung die Einstelleinrichtung für das Verschwenken des den auf kleinerem Teilkreisdurchmesser angeordneten Kolben zugeordneten Schrägscheibenkörpers derart auszugestalten, daß durch diese Einstelleinrichtung zusätzlich ein kleines Verschwenken dieses Schrägscheibenkörpers um eine zweite, zu der ersten Schwenkachse und der Drehachse der Zylindertrommel senkrecht stehende Achse bewirkt werden kann. Ein solche kleine, willkürlich herbeigeführte zusätzliche Verschwenkung um die zweite Schwenkachse ermöglicht, bei gleichgehaltener Lage der Trennstege im Steuerdrehschieber eine kleine Vorkompression bzw. Vorexpansion während des Überschleifens der Trennstege zu erzielen und damit eine Verminderung der Betriebsgeräusche.In addition, according to a further step of the invention, the spherical bearing surface enables the adjustment device for the pivoting of the swash plate body associated with the piston arranged on a smaller pitch circle diameter to be designed in such a way that this adjustment device additionally swivels this swash plate body a small amount about a second, to the first pivot axis and the axis of rotation vertical axis of the cylinder drum can be effected. Such a small, arbitrarily brought about additional pivoting about the second pivot axis makes it possible to achieve a small pre-compression or pre-expansion while smoothing over the separating webs while keeping the separating webs in the control rotary valve in the same position and thus avoiding them operating noise.

Gemäß einem weiteren Schritt der Erfindung ist eine Verbindungseinrichtung vorgesehen, durch die die an sich im Betrieb unabhängig voneinander einstellbaren Schrägscheibenkörper während bestimmter Betriebszustände willkürlich zwecks gemeinsamer Verstellung miteinander verbindbar sind. Das heißt, in Betriebszuständen, in denen es gewollt ist, daß die Förderströme beider Pumpen jeweils im gleichen Maße verändert werden, wird durch diese Verbindungseinrichtung die Verbindung hergestellt, wobei diese Verbindung lösbar ist, so daß in anderen Betriebszuständen das Ziel, zwei voneinander unabhängige Förderströme zu erzeugen, verfolgt werden kann.According to a further step of the invention, a connecting device is provided, by means of which the swash plate bodies, which can be adjusted independently of one another during operation, can be arbitrarily connected to one another for the purpose of common adjustment during certain operating states. That is, in operating states in which it is desired that the flow rates of both pumps are changed to the same extent, the connection is established by this connecting device, this connection being releasable, so that in other operating states the goal is two independent flow rates to generate can be tracked.

In einer zweckmäßigen Ausgestaltungsform ist vorgesehen, daß der den auf kleinerem Teilkreisdurchmesser angeordneten Kolben zugeordnete Schrägscheibenkörper mit einem durch eine Ausnehmung des den auf größerem Teilkreisdurchmesser angeordneten Kolben zugeordneten Schrägscheibenkörpers hindurchgreifenden Stellglied eines Stellorganes in Wirkverbindung steht, das heißt, die Verstellung des den auf kleinerem Teilkreisdurchmesser angeordneten Kolben zugeordneten Schrägscheibenkörpers erfolgt nicht durch eine parallel zur Drehachse angreifende Einrichtung, sondern durch eine Einrichtung, die durch den äußeren Schrägscheibenkörper hindurchgreift.In an expedient embodiment, it is provided that the swash plate body assigned to the piston arranged on a smaller pitch circle diameter is in operative connection with a swash plate body which extends through a recess of the swash plate body assigned to the piston arranged on a larger pitch circle diameter, that is to say the adjustment of the one arranged on the smaller pitch circle diameter Piston-associated swash plate body is not provided by a device that acts parallel to the axis of rotation, but by a device that extends through the outer swash plate body.

Weiterhin ist in einer zweckmäßigen Weiterausgestaltung die Möglichkeit vorgesehen, daß beide Schrägscheibenkörper eine zentrale Ausnehmung aufweisen, durch die die mit der Zylindertrommel verbundene Welle zu einem freien Anschluß hindurchragt.Furthermore, in an expedient refinement, the possibility is provided that both swashplate bodies have a central recess through which the shaft connected to the cylinder drum projects to a free connection.

In der Zeichnung ist ein Ausführungsbeispiel des Erfindungsgegenstandes dargestellt.In the drawing, an embodiment of the subject of the invention is shown.

An das Gehäusemittelteil ist einerseits der Steuerboden 2 und andererseits der Wiegenlagerteil 3 angebaut. Diese Teile sind durch in der Zeichnung nicht dargestellte Ankerschrauben miteinander verbunden.The control base 2 and the cradle bearing part 3 are attached to the middle part of the housing. These parts are connected to each other by anchor bolts, not shown in the drawing.

Im Gehäusemittelteil 1 ist die Zylindertrommel 4 mittels eines Wälzlagers 55 gelagert. Mit ihrer Stirnfläche 5 liegt die Zylindertrommel 4 gegen eine Steuerplatte 6 an, die ihrerseits drehfest am Steuerbodenteil2 gelagert ist. Die Zylindertrommel 4 weist eine Längsbohrung 7 auf, die in ihrem in der Zeichnung linken Teil mit einer Innenverzahnung 8 versehen ist, die in die Verzahnung einer Triebwelle eingreift, die ihrerseits mittels eines Lagers 10 (das vorzugsweise als Wälzlagerpaar gestaltet ist) in dem Steuerboden 2 gelagert ist. Der Deckel 12 dient zur Sicherung des Lagers 10 und trägt die Dichtung 11.The cylinder drum 4 is mounted in the middle part 1 of the housing by means of a roller bearing 55. With its end face 5, the cylinder drum 4 bears against a control plate 6, which in turn is rotatably mounted on the control base part 2. The cylinder drum 4 has a longitudinal bore 7 which, in the part on the left in the drawing, is provided with an internal toothing 8 which engages in the toothing of a drive shaft which in turn by means of a bearing 10 (which is preferably designed as a pair of roller bearings) in the control floor 2 is stored. The cover 12 serves to secure the bearing 10 and carries the seal 11.

Koaxial zur Welle 9 ist ein Zapfen 13 vorgesehen, der einen Bund 14 und einen Kugelkopf 15 aufweist. Gegen den Bund 14 ist ein Tellerfederpaket 16 gestützt, welches andererseits gegen die Zylindertrommel4 abgestützt ist. Der Kugelkopf 15 liegt in einer entsprechenden Ausnehmung der Andrückplatte 17, die Bohrungen aufweist, durch die die Gleitschuhe 18 der auf kleinem Teilkreisdurchmesser angeordneten Kolben 19 hindurchragen. Die Gleitschuhe 18 weisen ein Basisteil20 auf, gegen das die Andrückplatte 17 drückt.A pin 13 is provided coaxially to the shaft 9 and has a collar 14 and a ball head 15. A plate spring assembly 16 is supported against the collar 14, which is supported on the other hand against the cylinder drum 4. The ball head 15 lies in a corresponding recess in the pressure plate 17, which has bores through which the sliding shoes 18 of the pistons 19, which are arranged with a small pitch circle diameter, protrude. The sliding shoes 18 have a base part 20 against which the pressure plate 17 presses.

Die auf kleinerem Teilkreisdurchmesser angeordneten Kolben 19 sind in Zylinderbohrungen 21 verschiebbar, wobei jede Zylinderbohrung 21 mit einem Mündungskanal 22 versehen ist, der in der Stirnfläche 5 der Zylindertrommel 4 mündet und zwar gegenüber einem zumindest annähernd halbkreisförmigen Kanal 23 in der Steuerplatte 6, der sich in einem Kanal 24 im Steuerboden 2 fortsetzt, wobei der Kanal 24 zu einem in der Zeichnung nicht dargestellten, neben der Zeichenebene liegenden Anschluß führt.The pistons 19, which are arranged on a smaller pitch circle diameter, are displaceable in cylinder bores 21, each cylinder bore 21 being provided with an orifice channel 22 which opens into the end face 5 of the cylinder drum 4, specifically in relation to an at least approximately semicircular channel 23 in the control plate 6, which is located in continues a channel 24 in the control floor 2, the channel 24 leading to a connection, not shown in the drawing, lying next to the plane of the drawing.

Die Kolben 25 sind auf einem größeren Teilkreisdurchmesser angeordnet als die Kolben 19, wobei jeder der Kolben 25 in einer Zylinderbohrung26 verschiebbar ist, die einen Mündungskanal 27 aufweist, wobei die Mündungskanäle 27 einem annähernd halbkreisförmigen Kanal 28 in der Steuerplatte 6 gegenüberliegen, wobei der Kanal 28 an einen Kanal 29 im Steuerbodenteil 2 anschließt, der zu einem Anschlußflansch 30 für eine in der Zeichnung nicht dargestellte Förderdruckleitung führt.The pistons 25 are arranged on a larger pitch circle diameter than the pistons 19, each of the pistons 25 being displaceable in a cylinder bore 26 which has an orifice channel 27, the orifice channels 27 being opposite an approximately semicircular channel 28 in the control plate 6, the channel 28 connects to a channel 29 in the control floor part 2, which leads to a connecting flange 30 for a delivery pressure line, not shown in the drawing.

Jeder Kolben 25 ist gegen einen Gleitschuh 31 abgestützt, dessen Basisteil32 durch einen Niederhaltering 33 gegen die Schrägscheibe 34 gedrückt wird, wobei der Niederhaltering 33 durch einen Anpreßring 35, der gegen den Schrägscheibenkörper 36 angeschraubt ist, gehalten ist. Die den auf größerem Teilkreisdurchmesser angeordneten Kolben 25 zugeordnete Schrägscheibe 34 ist also an dem Schrägscheibenkörper 36 gebildet. Dem gegenüber sind die auf kleinerem Teilkreisdurchmesser angeordneten Kolben 19 mittels ihrer Gleitschuhe 18 gegen die Schrägscheibe 37 abgestützt, die an dem Schrägscheibenkörper 38 gebildet ist und der auf seiner Rückseite eine kugelkappenförmige Fläche 39 aufweist, die in einer hohlkugeligen Fläche des Schrägscheibenkörpers 36 ruht. Der Schrägscheibenkörper 36 weist auf einer Rückseite eine halbzylindrische Fläche 40 auf, die in einer hohlzylindrischen Fläche des Wiegenlagerungsteiles 3 ruht.Each piston 25 is supported against a slide shoe 31, the base part 32 of which is pressed against the swash plate 34 by a hold-down ring 33, the hold-down ring 33 being held by a pressure ring 35 which is screwed against the swash plate body 36. The swash plate 34 assigned to the piston 25 arranged on a larger pitch circle diameter is thus formed on the swash plate body 36. In contrast, the pistons 19, which are arranged on a smaller pitch circle diameter, are supported by means of their sliding shoes 18 against the swash plate 37, which is formed on the swash plate body 38 and has a spherical cap-shaped surface 39 on its rear side, which rests in a hollow spherical surface of the swash plate body 36. The swash plate body 36 has a semi-cylindrical surface 40 on a rear side, which rests in a hollow cylindrical surface of the cradle bearing part 3.

Der Schrägscheibenkörper 36 weist eine Ausnehmung 41 auf, durch die ein Stellzapfen 42 hindurch greift, der mit einem Kugelkopf 43 versehen ist, der in einer Bohrung 64 des Schrägscheibenkörpers 38 geführt ist. Der Stellzapfen 42 ist andererseits in dem Stellkolben 44 befestigt, der in dem Stellzylinder45 verschiebbar ist, der in einem entsprechenden Fortsatz des Wiegenlagerungsteiles 3 gebildet ist und beiderseits durch je einen Deckel46 verschlossen ist, durch den jeweils in der Zeichnung nicht dargestellte Druckflüssigkeitsleitungen hindurchführen, mittels derer der Stellkolben 44 willkürlich mit Druckmittel beaufschlagbar ist.The swashplate body 36 has a recess 41 through which an adjusting pin 42 extends, which is provided with a ball head 43 which is guided in a bore 64 in the swashplate body 38. The adjusting pin 42 is on the other hand fastened in the adjusting piston 44, which is displaceable in the adjusting cylinder 45, which is formed in a corresponding extension of the cradle bearing part 3 and is closed on both sides by a cover 46, through which the hydraulic fluid lines, not shown in the drawing, pass, by means of which the actuating piston 44 can be acted upon arbitrarily with pressure medium.

Am Wiegenlagerungsteil 3 ist ein weiterer Fortsatz gebildet, in dem ein Stellzylinder47 angeordnet ist, in dem ein Stellkolben 48 verschiebbar ist. Auch der Stellzylinder47 ist durch zwei Decket 46 abgeschlossen. Im Stellkolben 48 ist ein Stellzapfen 49 befestigt, der mit seinem Kugelkopfteil50 in eine Bohrung 51 des Schrägscheibenkörpers 36 eingreift.A further extension is formed on the cradle bearing part 3, in which an actuating cylinder 47 is arranged, in which an actuating piston 48 is displaceable is. The actuating cylinder 47 is also closed by two covers 46. A setting pin 49 is fastened in the adjusting piston 48 and engages with its spherical head part 50 in a bore 51 of the swash plate body 36.

Bei der in der Zeichnung dargestellten Ausgestaltungsform der Doppelpumpe für zwei offene Kreisläufe ist im Steuerbodenteil 2 ein Saugkanal 52 vorgesehen, der vor einer weiten Öffnung 53 der Steuerplatte 6 mündet, wobei die Öffnung 53 sich in radialer Richtung so weit erstreckt, daß sie sowohl vor den Mündungskanälen 27 als auch vor den Mündungskanälen 22 liegt. In Umfangsrichtung erstreckt sich die Öffnung 53 ebenso weit wie die annähernd halbkreisförmigen Kanäle 23 und 28 auf der anderen Seite.In the embodiment of the double pump for two open circuits shown in the drawing, a suction channel 52 is provided in the control floor part 2, which opens into a wide opening 53 of the control plate 6, the opening 53 extending in the radial direction so far that it both before the Mouth channels 27 and in front of the mouth channels 22. In the circumferential direction, the opening 53 extends just as far as the approximately semicircular channels 23 and 28 on the other side.

In einer abgewandelten Ausgestaltungsform können auch vor der Mündung des Saugkanales 52 zwei annähernd halbkreisförmige Kanäle gebildet sein, die den Kanälen 23 und 28 entsprechen, wobei die dem Saugkanal 52 zugewandte Seite der Steuerplatte 6 strömungsgünstig gestaltet ist. In einer anderen Abwandlung der Ausgestaltungsform ist das Steuerbodenteil 2 auf beiden Seiten symetrisch gestaltet, das heißt anstelle des Saugkanales 52 und der Öffnung 53 sind zwei getrennte Kanäle im Steuerbodenteil 2 und entsprechend zwei annähernd halbkreisförmige Kanäle entsprechend den Kanälen 23 und 28 in der Steuerplatte 6 gebildet, so daß die Pumpe für zwei geschlossene Kreisläufe ausgestaltet ist.In a modified embodiment, two approximately semicircular channels can also be formed in front of the mouth of the suction channel 52, which channels correspond to the channels 23 and 28, the side of the control plate 6 facing the suction channel 52 being designed to be streamlined. In another modification of the embodiment, the control floor part 2 is designed symmetrically on both sides, that is, instead of the suction channel 52 and the opening 53, two separate channels are formed in the control floor part 2 and correspondingly two approximately semicircular channels corresponding to the channels 23 and 28 in the control plate 6 , so that the pump is designed for two closed circuits.

In der üblichen Weise ist der Steuerbodenteil 2 um 90° um die Achse der Welle 9 verdreht gezeichnet, weil in der Schnittebene, die senkrecht auf der Schwenkachse der Schrägscheibenkörper 36 und 38 steht, in der Steuerplatte 6 die Trennstege liegen, also keine Öffnungen in der Zeichnung zu erkennen wären, wenn der Schnitt durch diese gelegt wäre.In the usual way, the control base part 2 is shown rotated by 90 ° about the axis of the shaft 9, because in the cutting plane, which is perpendicular to the swivel axis of the swash plate bodies 36 and 38, the separating webs lie in the control plate 6, that is to say no openings in the The drawing would be recognizable if the cut were placed through it

Claims (6)

1. An axial piston pump for the production of two output streams, the magnitude of which can be adjusted independently of one another, said pump having a revolving cylindrical drum (4) which is connected to a shaft (9), and in which are arranged cylindrical bores (21 and 26), all of which open into the same end face (5) of the cylindrical drum (4), wherein a piston (19 or 25) is displaceable in each cylindrical bore (21 or 26), wherein the cylindrical bores (21 and 26) in the cylindrical drum (4) are arranged at two different pitch circle diameters, wherein the pistons (19) in the cylinders (21) arranged at the smaller pitch circle diameter rest against an adjustable tilting disc (37) formed on a tilting disc body (38), and the pistons (25) in the cylinders (26) arranged at the larger pitch circle diameter rest against a second adjustable tilting disc (34) which is formed on a second tilting disc body (36), wherein each of the two tilting discs (34 and 37) is connected to an adjusting device, consisting of an adjusting means (44 or 48) and an adjusting member (42 or 49), which serves to adjust the pivoting of the tilting disc body (36 or 38) about a pivotal axis which is at right angles to the axis of rotation of the cylindrical drum (4) in order to set the inclination of the tilting disc (34 or 37), relative to the axis of rotation of the cylindrical drum (4), which determines the stroke of the assigned piston (19 or 25), wherein, at the end face of the cylindrical drum (4) which lies opposite to the end face of the cylindrical drum (4) at which the pistons (19, 25) emerge, there is formed a rotary slide control valve, wherein in this end face of the cylindrical drum (4), channels (22) open at a pitch circle diameter, which are connected to the cylindrical bores (21) arranged at a smaller pitch circle diameter, and at a larger pitch circle diameter, there are arranged channels (27) which are connected to the cylinder bores (26) arranged at a larger pitch circle diameter, wherein opposite this end face of the cylindrical drum (4), there is arranged a control plate (6) in which two approximately semi-circular annular channels (23) are arranged at a pitch circle diameter corresponding to the pitch circle diameter of the channels (22), and two further approximately semicircular annular channels are arranged at a pitch circle diameter which corresponds to the pitch circle diameter of the channels (27), characterised in that the tilting disc body (38), on which is formed the tilting disc (37) against which rest the pistons (19) arranged at a smaller pitch circle diameter, has at its side facing away from the tilting disc (37) a calotte-shaped surface, with which surface (39), it is mounted in a calotte-shaped recess in the tilting disc body (36) on which is formed the tilting disc (34) against which rest the pistons (25) arranged at a larger pitch circle diameter.
2. An axial piston pump according to Claim 1, characterised in that the adjusting means (44) and the adjusting member (42) of the adjusting device which adjusts the pivoting about its pivotal axis of the tilting disc body (38) which is assigned to the pistons (19) arranged on a smaller pitch circle diameter, are such that this adjusting device can additionally produce a small pivoting of this tilting disc body (38) about a second axis which is at right angles to the first-mentioned pivotal axis and to the axis of rotation of the cylindrical drum (4).
3. An axial piston pump according to Claim 2, characterised in that the bearing and the adjusting device consisting of the adjusting means (48) and adjusting member (49) which serves to adjust the tilting disc body (36) assigned to the pistons (25) arranged at the larger pitch circle diameter, is also arranged to effect a pivotal motion about two axes which are at right angles to one another.
4. An axial piston pump according to Claim 1, characterised by a connecting device by means of which the two tilting disc bodies (38 and 36), which can be adjusted independently of one another, can be detachably connected at will in order to effect a common adjustment for specific operating states.
5. An axial piston pump according to Claim 1, characterised in that the tilting disc body (38) which is assigned to the pistons (19) arranged at a smaller pitch circle diameter, is actively connected to an adjusting member (42, 43) of an adjusting means (45, 44), which member (42, 43) passes through an aperture (41) in the tilting disc body (36) which is assigned to the pistons (25) arranged on a larger pitch circle diameter.
6. An axial piston pump according to one of the preceding Claims, characterised in that both the tilting disc bodies have a central recess through which the shaft connected to the cylindrical drum (4) projects for a free shaft connection.
EP81105478A 1980-07-15 1981-07-13 Axial piston pump with two delivery streams Expired EP0044070B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3026765 1980-07-15
DE19803026765 DE3026765A1 (en) 1980-07-15 1980-07-15 AXIAL PISTON PUMP FOR TWO FLOWERS

Publications (2)

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EP0044070A1 EP0044070A1 (en) 1982-01-20
EP0044070B1 true EP0044070B1 (en) 1984-02-08

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EP81105478A Expired EP0044070B1 (en) 1980-07-15 1981-07-13 Axial piston pump with two delivery streams

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US (1) US4449444A (en)
EP (1) EP0044070B1 (en)
JP (1) JPS5751343A (en)
DE (1) DE3026765A1 (en)

Families Citing this family (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3134537C2 (en) * 1981-09-01 1986-03-27 Moskovskoe naučno-proizvodstvennoe ob"edinenie po stroitel'nomu i dorožnomu mašinostroeniju VNIISTROIDORMAŠ, Moskva Hydraulic axial piston machine with rotating displacement bodies
DE3212429A1 (en) * 1982-04-02 1983-10-13 Abex Corp., 10036 New York, N.Y. HYDRAULIC AXIAL PISTON MACHINE
GB2134188B (en) * 1983-01-27 1986-09-10 Linde Ag An adjustable axial piston machine of the inclined swash plate type
DE3333812C2 (en) * 1983-09-19 1986-08-07 Hydromatik GmbH, 7915 Elchingen Swivel drum axial piston machine
US4710107A (en) * 1986-04-15 1987-12-01 The Oilgear Company Swashblock lubrication in axial piston fluid displacement devices
DE3725525A1 (en) * 1987-07-31 1989-02-09 Linde Ag ADJUSTABLE AXIAL PISTON MACHINE IN SLOPED AXIS DESIGN
DE4027794C2 (en) * 1990-09-01 2002-06-20 Continental Teves Ag & Co Ohg Hydraulic radial piston pump
US7007589B1 (en) 1997-09-15 2006-03-07 R. Sanderson Management, Inc. Piston assembly
US6460450B1 (en) 1999-08-05 2002-10-08 R. Sanderson Management, Inc. Piston engine balancing
US6446587B1 (en) * 1997-09-15 2002-09-10 R. Sanderson Management, Inc. Piston engine assembly
DE19947321A1 (en) * 1999-10-01 2001-04-19 Brueninghaus Hydromatik Gmbh Axial piston machine has a supporting part fixed to a bearing surface of a housing using screws arranged longitudinally with respect to the rotating axis and screwed into a threaded bore
DE10055262A1 (en) * 2000-11-08 2002-05-23 Linde Ag Hydrostatic axial piston machine in inclined disc construction method
US7011469B2 (en) * 2001-02-07 2006-03-14 R. Sanderson Management, Inc. Piston joint
US7331271B2 (en) 2001-02-08 2008-02-19 R. Sanderson Management, Inc. Variable stroke/clearance mechanism
US6854377B2 (en) 2001-11-02 2005-02-15 R. Sanderson Management, Inc. Variable stroke balancing
US6913447B2 (en) * 2002-01-22 2005-07-05 R. Sanderson Management, Inc. Metering pump with varying piston cylinders, and with independently adjustable piston strokes
WO2003100231A1 (en) * 2002-05-28 2003-12-04 R. Sanderson Management, Inc. Overload protection mecanism
DE10349599B3 (en) * 2003-10-24 2005-07-07 Brueninghaus Hydromatik Gmbh Connection block for a hydrostatic piston engine
DE10358728B4 (en) * 2003-12-15 2006-01-05 Brueninghaus Hydromatik Gmbh Axial piston machine for independent pumping in several hydraulic circuits
US7438029B2 (en) * 2004-03-18 2008-10-21 R. Sanderson Management, Inc. Piston waveform shaping
JP4808708B2 (en) * 2004-05-26 2011-11-02 アール サンダーソン マネージメント インコーポレイテッド Variable stroke and clearance mechanism
DE102006021570A1 (en) * 2006-04-10 2007-10-18 Robert Bosch Gmbh Hydrostatic piston machine with rotating control disc
US20100028169A1 (en) * 2008-07-31 2010-02-04 Caterpillar Inc. Hydraulic device having an alignment component
DE102011077253A1 (en) * 2011-06-09 2012-12-13 Robert Bosch Gmbh Axial piston machine in swash plate design
DE102013200729A1 (en) * 2013-01-18 2014-07-24 Robert Bosch Gmbh Swash plate machine
US9803634B2 (en) * 2014-09-05 2017-10-31 Caterpillar Inc. Valve plate arrangement for an axial piston pump
CN104358657A (en) * 2014-11-03 2015-02-18 安徽理工大学 Two-side driving balance type low-speed large-torque axial plunger motor
NL2014672B1 (en) * 2015-04-20 2017-01-20 Forage Innovations Bv Hydraulic fluid distributor and hydraulic fluid distributing method.
DE102021200205A1 (en) 2021-01-12 2022-07-14 Robert Bosch Gesellschaft mit beschränkter Haftung Axial piston machine with high drive speed
CN115523115B (en) * 2022-09-29 2024-04-19 燕山大学 Top-to-top ultra-high pressure axial piston pump
DE102023204123A1 (en) * 2023-05-04 2024-11-07 Robert Bosch Gesellschaft mit beschränkter Haftung Axial piston machine with variable pressure fields on the sliding shoes

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1714148A (en) * 1927-12-21 1929-05-21 Weldy Arthur Sheldon Pump
US2520632A (en) * 1945-03-22 1950-08-29 Torq Electric Mfg Company Hydraulic pump or motor
US2445281A (en) * 1945-10-04 1948-07-13 Charles H Rystrom Hydraulic pump
DE1129828B (en) * 1959-09-18 1962-05-17 Citroen Sa High pressure axial piston pump with rotating cylinder drum and swiveling swivel plate
FR1340850A (en) * 1962-07-19 1963-10-25 Improvements to piston pumps and the like
CH445298A (en) * 1962-10-09 1967-10-15 Hydrospeed Ag Retraction device for hydraulic axial piston machines
GB1073216A (en) * 1962-11-21 1967-06-21 F W Baggett & Co Ltd Improvements relating to swash plate pumps and motors
FR1415392A (en) * 1964-12-03 1965-10-22 Karl Marx Stadt Ind Werke Hydraulic axial piston machine
DE1625073C3 (en) * 1967-05-09 1978-05-24 Detlef 7531 Kieselbronn Hofmann Pressure fluid operated piston machine
GB1176621A (en) * 1968-01-09 1970-01-07 Karl Marx Stadt Ind Werke Improvements in or relating to Reciprocating Hydraulic Pumps or Motors
DE2451380C2 (en) * 1974-10-29 1985-08-14 Linde Ag, 6200 Wiesbaden Adjustable axial piston motor with a swivel vane actuator
IT1082968B (en) * 1977-04-05 1985-05-21 Gherner Lidio HYDRAULIC AXIAL PISTON MOTOR
SU804858A1 (en) * 1977-12-09 1981-02-15 Уральский Ордена Трудового Красногознамени Политехнический Институтимени C.M.Кирова Axial-piston hydraulic machine

Also Published As

Publication number Publication date
EP0044070A1 (en) 1982-01-20
JPS5751343A (en) 1982-03-26
US4449444A (en) 1984-05-22
DE3026765A1 (en) 1982-02-11

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