EP0320822B2 - Axial piston pump - Google Patents

Axial piston pump Download PDF

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Publication number
EP0320822B2
EP0320822B2 EP88120650A EP88120650A EP0320822B2 EP 0320822 B2 EP0320822 B2 EP 0320822B2 EP 88120650 A EP88120650 A EP 88120650A EP 88120650 A EP88120650 A EP 88120650A EP 0320822 B2 EP0320822 B2 EP 0320822B2
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EP
European Patent Office
Prior art keywords
axial piston
piston pump
pistons
pump according
control
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP88120650A
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German (de)
French (fr)
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EP0320822A1 (en
EP0320822B1 (en
Inventor
Heinz Berthold
Ivan Pecnik
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Brueninghaus Hydraulik GmbH
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Brueninghaus Hydraulik GmbH
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Application filed by Brueninghaus Hydraulik GmbH filed Critical Brueninghaus Hydraulik GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2042—Valves

Definitions

  • the invention relates to an axial piston pump according to DE-C-3233579, from which the preamble of claim 1 is based.
  • Such an axial piston pump can be adapted to the desired delivery direction.
  • Such an embodiment is not only very complex, precisely because two connection parts are to be provided, but also requires storage effort with regard to the connection part not used in each case in order to have it available if required.
  • the invention has for its object to design an axial piston pump of the type mentioned so that it can be adapted to the other direction of delivery with less effort.
  • the axial piston pump can be adjusted by rotating the control part consisting of the control disk and the connecting part through 180 ° to the desired delivery direction. There is therefore no need for an additional connecting part or an additional control disk, as is the case with the known configurations.
  • the connection part is rotated, there is a displacement of the suction and discharge openings with respect to the axial piston pump or the machine receiving it, however, this problem can be solved in a simple manner by using flexible connecting lines or suitable connecting line sections.
  • the invention also makes it possible to adapt such axial piston pumps, the control disks of which are designed asymmetrically with respect to the control openings (control kidneys) or have so-called pressure compensation channels in a manner known per se.
  • the retrofitting of the axial piston pump according to the invention is very simple because it only requires a solution and removal of the existing fastening screws for the connecting part.
  • the connecting part and the control disk can then be rotated in a simple manner by 180 °, an advantageously existing centering projection with a round cross section between the connecting part and the housing of the axial piston pump serving as a rotary bearing.
  • the configuration according to the invention is suitable for those axial piston pumps in which the delivery direction is changed by changing the direction of rotation of the drive shaft or, in the case of axial piston pumps, adjustable delivery rate by adjusting the adjusting device beyond the zero point.
  • a simple and practical channel guide for loading the adjusting device of the axial piston pump is proposed, which is functional and advantageous in both mounting positions of the connecting part.
  • the swash plate is pivoted out by the engine forces of the axial piston pump, so that no additional pivoting mechanism is required.
  • the swash plate is simple and easy to assemble or disassemble.
  • the features of claim 10 ensure simple and inexpensive manufacture, the bearing bodies being able to be produced from finished balls by reworking such as turning.
  • Claims 11 and 12 relate to mechanical stops, in particular to prevent the swivel plate from overshooting when swiveling in at high positioning speeds.
  • the bearing that is more heavily loaded is starting from the slideway of the swash plate, intermittent and from the height of the operating pressure is supplied with pressure oil by the pistons and is therefore advantageously lubricated.
  • This design enables low-friction and low-wear operation with fast operating times.
  • the axial piston pump generally designated 1 in FIG. 1, has a two-part one made of a cup-shaped one Housing part 2 and a connection plate 3 existing housing in which a drive shaft 5 extending along the central axis 4 is mounted in roller bearings 6, 7, one of which is assigned to the cup-shaped housing part 2 and the other of the connection plate 3 is on the drive shaft 5 on a multi-wedge section denoted by 8, a cylinder drum 9 is mounted, which has a plurality of cylinder bores 11, evenly distributed on a pitch circle, in which pistons 12 are received.
  • the pistons 12 have ball heads 13 which engage in sliding shoes 14 which bear against the sliding surface 15 of a swash plate 16.
  • a retraction plate 17 which, in the present exemplary embodiment, is mounted on a spherical head-shaped carrier piece 19 with a recess 18 in the form of a spherical segment.
  • the carrier piece 19 is mounted on the drive shaft 5 so as to be longitudinally displaceable.
  • the swash plate 16 is mounted about a swivel axis 22 in a swivel bearing which is formed by two supports, generally designated 23, lying one behind the other along the swivel axis 22, consisting of two mushroom-shaped bearing pieces 24 which, with their round cross-section pin 25 in bores 26 in Bottom of the cup-shaped housing part 2 are inserted and surround in spherical recesses 27 on the back of the swash plate 16.
  • the spherical convex surfaces of the bearing pieces 24 facing the pistons and the spherical concave surfaces of the recesses 27 thus form housing-side and swashplate-side bearing surfaces 28.
  • pan-shaped bearing shells 29 are used in the recesses 27, each with a radially projecting collar 31 on the peripheral edge of the Recesses 27 abut and are thus secured against tilting movements.
  • the pivot axis 22 of the swash plate 16 is located at a distance a from the line of action of the piston force 32 resulting from the forces of the active pistons 12, this distance a extending beyond the central axis 4.
  • the resulting piston force 32 is generated by the pistons 12 located on the respective pressure side. Due to the distance a, the swash plate 16 is loaded counterclockwise with a torque according to FIG of the cup-shaped housing part 2 arranged and in cylinder bores 34 axially parallel to the drive shaft 5, ie are hydraulically displaceable in the direction of the double arrow 35.
  • the adjusting pistons 33 are arranged opposite the effective resulting piston force 32, i.e.
  • the swash plate 16 In the position shown in FIG. 1, the swash plate 16 is in its maximum piston stroke position. By extending the actuating piston 33, the swash plate 16 can be adjusted about the pivot axis 22 in either pivot positions or delivery quantity settings. To limit the maximum pivoting position, stops 37 are arranged on both sides of the axial transverse plane 36 approximately opposite the actuating pistons 33, which are formed by bolts or screws 38 with stop pins inserted laterally into the housing part 2 from the outside. When bearing against the stops 37, the axial piston machine 1 is set to a minimum piston stroke and a minimum delivery rate.
  • the pivot bearings 23 are each connected to the oil-carrying system of the axial piston machine 1 by a lubrication channel 39 which extends from the recess 27 and crosses the bearing shell 29 and the swash plate 16 and is thus oil-lubricated.
  • the lubrication channel 39 opens into the sliding surface 15 of the swash plate 16 in the vicinity of the pitch circle on which the pistons 12 are arranged, specifically in an area which the sliding shoes 14 cover with a recess 41 in their sliding surface 42.
  • the recess 41 is connected to the working spaces 45 of the piston cylinders by means of axially known channels 43, 44 in the sliding shoes 14 and the pistons 12. In this way, when the axial piston pump 1 is in operation, the bearing point of the pivot bearing 23 which is subjected to higher loads is intermittently supplied with lubricating oil under working pressure when the sliding shoes 14 are swept over.
  • the cylinder drum 9 lies with its end facing away from the swashplate 16 against a control plate 46 which is arranged between the cylinder drum 9 and the connection plate 3 and is held on the connection plate 3 in a rotationally fixed manner about the central axis 4.
  • the control plate 46 shown in detail in FIG. 3 has two essentially kidney-shaped control openings 47, 48 penetrating it, to which kidney-shaped suction or pressure channels 51, 52 also adjoin in the connecting plate 3, of which the suction channel 51 is opposite the pressure channel 52 with an enlarged end cross section, namely a large suction opening 53, here a connection for a suction line, not shown.
  • the control kidney 48 is interrupted on the pressure side by reinforcing webs 50.
  • Known pressure compensation notches 55, 56 are arranged at the ends of the control kidneys 47, 48, which are opposite to the respective direction of rotation, which is exemplified by the arrow 54 in FIG. 3, the purpose of which is to improve the sudden effect of the pressure changes in the working spaces 45 to be reduced if the control channels 57 which are present in the cylinder drum 9 and extend from the working spaces 45 come into contact with the control kidneys 47, 48 containing high or low pressure.
  • the control plate 46 has pressure compensation notches 56 on both sides, namely at one and the same end of at least the high-pressure control kidney 48. That is, on the rear of the control plate 46 according to FIG. 3 there are also pressure compensation notches 55, 56 behind the visible pressure compensation notches 55 , 56 available.
  • the pressure compensation notches 55, 56 extend from the relevant end of the control kidneys 47, 48 and converge in a wedge shape, as shown in the partial section according to FIG. 4.
  • the pressure compensation notches (s) 55 are optionally on both sides of the control plate 46, preferably in the direction of rotation 54 opposite end of the low-pressure control kidney 47 arranged.
  • the control plate 46 is secured against rotation by means of a pin connection with a pin 60 (FIG. 5) which preferably extends from the connecting plate 3 and which fits into a blind hole or through-hole 61 in the control plate 46.
  • control plate 46 can optionally be attached with its one or the other end face to the connection plate 3, namely it can be folded essentially about a transverse axis 58 parallel to the transverse axis 36 according to FIG. 2, so that the control kidneys 47 , 48 always correspond to the likewise kidney-shaped suction or pressure channels 51, 52 in the connection plate 3.
  • the arrangement of the pin 60 and a pin hole 61 which receives the pin 60 and passes through here is preferably such that the two optional mounting positions of the control plate 46 differ with respect to the position predetermined by the connecting plate 3, namely that one mounting position is opposite the one another mounting position offset in the circumferential direction, which is illustrated by the angle b shown in FIG.
  • control kidneys 47, 48 are not symmetrical with respect to the arrangement predetermined by the control channels 57, namely for functional reasons in order to achieve a certain advance, which is known per se.
  • the angle b 1 in FIG. 3 shows the angular offset in the folded mounting position of the control plate 46.
  • control plate 46 is configured in parallel.
  • the cylinder drum 9 is rotated by the drive shaft 5.
  • the cylinder bores 11 are mutually connected to the control kidneys 47, 48 via the control channels 57, as a result of which the pumping action results in a known manner due to the movement of the pistons 12.
  • the direction of flow of the hydraulic medium is illustrated in FIG. 1 by arrows 62 and 63.
  • the seal between the cylinder drum 9 and the control plate 46 is ensured by a compression spring 64 which is clamped between an inner ring 65 of the cylinder drum 9 and a pressure ring.
  • At least one axial pressure element in the present exemplary embodiment extends in the form of three pressure pins 66 distributed around the circumference, which are axially displaceable in a guide of the cylinder drum 9, between the pressure ring and the carrier piece 19.
  • the compression spring 64 By means of the compression spring 64, the cylinder drum 9 is thus elastically acted against the control plate 46 and the carrier piece 19 against the retraction plate 17 and consequently also the swash plate 16 against the support 23.
  • a comparable purpose could also advantageously be achieved by e.g. compression springs arranged in the cylinder bores 11 are applied, which act on the pistons 12 in the direction of the swash plate 16.
  • connection plate 3 is designed such that it can be mounted rotated by 180 ° about the central axis 4. This applies in particular to the four fastening screws 67 evenly distributed on a pitch circle in the present exemplary embodiment and the configurations relating to the control arrangement such as the kidney-shaped suction or pressure channel sections 51, 52, the pin connection between the connection plate 3 and the control plate 46 and the general with 68 designated centering with a round in cross-section 69 on the connecting plate 3, which roughly surrounds the cavity 71 of the housing, which is also round in cross-section.
  • the connection plate 3 can thus be rotated and loosened after loosening and removing the fastening screws 67 by 180 °.
  • the axial piston machine 1 can be adapted in a simple manner to a reversal of the conveying direction, and indeed the larger suction opening 53 in cross section can be arranged in the position predetermined by the reversal of the flow direction, namely optionally on one or the other side of the axial piston machine 1, so that trouble-free suction or trouble-free filling of the suction piston cylinders is achieved.
  • connection plate 3 is made of drawn profile material, preferably a square cross-section. This enables cost-effective production.
  • the fastening screws 67 are arranged in an opposite position in the corner region of the connection plate 3.
  • the assembly or disassembly of the swash plate 16 is very simple because after removing the Connection plate 3 both individually and on the drive shaft 5 as a pre-assembled unit inserted into the housing part 2 from the open side of the housing and can be removed again in the opposite direction.
  • a valve, generally designated 72, is provided for adjusting the delivery rate of the axial piston pump 1, with which it is possible to regulate the delivery rate setting as a function of the existing working pressure in such a way that the delivery rate decreases with increasing working pressure and the delivery rate increases with decreasing working pressure ( Pressure control) or the delivery rate is only limited depending on the pressure.
  • valve 72 is arranged in a line connecting the pressure channel 52 with the working spaces 73 of the adjusting cylinders, generally designated 74, in order to regulate or control the action on the adjusting pistons 33.
  • This connecting channel which consists of several sections and is designated by 75, is connected to the pressure channel 52 in the region of the connecting plate 3.
  • two connecting channel branches 76, 77 drilled and closed from the outside are in the connecting plate 3 (FIG. 5).
  • the one connecting channel branch 76 corresponds in one assembly position and the other connecting channel branch 77 in the other mounting position of the connecting plate 3 rotated by 180 ° at the interface designated 78 (FIG. 1) of the connecting channel 75.
  • This interface 78 is located in the parting line between the housing part 2 and the connecting plate 3, and it is sealed off from the parting line in a manner not shown.
  • the connecting channel 75 initially runs axially in the housing part 2 in the region of the valve 72, which is attached laterally and preferably symmetrically to an attachment surface 79 and is fastened in a manner not shown, the valve housing of which is generally designated 81.
  • the valve 72 has a valve slide 82 with a collar which has control edges on both sides and which forms a variable valve opening with a connecting channel section 87 extending from the bore 86 receiving the slide 82 to the working spaces 73.
  • the slide 82 is urged at its upper end in FIG. 1 by a spring 89 into a position closing the valve opening.
  • connecting channel branches 91, 92 (FIG. 2) in order to reduce or limit the delivery rate.
  • the connecting duct sections 91, 92 are each connected to the working spaces 73 of the adjusting cylinders 74 via a circumferential groove 93 and a radial and axial connecting duct section 94.95 (FIG. 1) in the adjusting piston 33.
  • venting channel sections 98, 99, 100 which are connected to the housing cavity 71 of the pump housing.
  • the ventilation duct section 98 is formed by the bore section 86 lying behind the collar, i.e. this ventilation duct section 98 starts from the valve opening and is closed when the adjusting piston 33 is acted upon by the collar.
  • the biasing force of the spring 89 can be adjusted by means of an adjusting screw 101, against which the spring 89 is supported via a spring actuator 102.
  • the adjusting screw 101 can be secured by a nut 103.
  • valve 72 It is possible within the scope of the invention to design the valve 72 and to arrange it in such a way that it can adjust the swash plate 16 between only two positions, namely between the maximum and minimum settings.
  • the larger suction opening 53, the smaller discharge opening 104, the suction and Pressure channels 51, 52 and the control kidneys 47, 48 in FIG. 1 are shown rotated by 90 ° in order to improve understanding, which is illustrated by a broken line.
  • the aforementioned design features lie on both sides of the transverse plane 36 (see FIG. 5), which also represents the sectional plane according to FIG. 1, and in which the transverse axis 58 also lies.
  • the reversal of the conveying direction is achieved by changing the direction of rotation of the drive shaft 5.
  • a reversal of the conveying direction can also be achieved in that the existing adjusting device of the axial piston pump, in contrast to the exemplary embodiment according to FIG. 1, can be adjusted beyond the zero point.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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Description

Die Erfindung bezieht sich auf eine Axialkolbenpumpe gemäß DE-C-3233579, von der auch der Oberbegriff des Anspruchs 1 ausgeht.The invention relates to an axial piston pump according to DE-C-3233579, from which the preamble of claim 1 is based.

Beim Einsatz einer Axialkolbenpumpe im offenen Kreislauf ergeben sich im Bereich der Ansaugöffnung der Axialkolbenmaschine Kavitationsschwierigkeiten, wenn nicht dafür gesorgt wird, daß eine befriedigende Menge des anzusaugenden hydraulischen Mediums bereitgestellt wird. Zur Lösung dieses Problems ist es bekannt, die Ansaugöffnung im Anschlußteil der Axialkolbenpumpe größer auszubilden als die druckseitige Abgabeöffnung. Durch diese Ausgestaltung ist die Förderrichtung der Axialkolbenmaschine vorbestimmt, und es ist deshalb nicht möglich, die Förderrichtung zu wechseln. Um eine solche Axialkolbenpumpe auch für beide Förderrichtungen einsetzen zu können, ist man dazu übergegangen, für die Axialkolbenpumpe zwei zueinander spiegelbildlich ausgestaltete Anschlußteile und entsprechende spiegelbildlich ausgestaltete Steuerscheiben vorzusehen. Durch Austausch der Anschlußteile kann eine solche Axialkolbenpumpe an die gewünschte Förderrichtung angepaßt werden. Eine Solche Ausgestaltung ist, eben weil zwei Anschlußteile vorzusehen sind, nicht nur sehr aufwendig, sondern es bedarf auch hinsichtlich des jeweils nicht eingesetzten Anschlußteils eines Lageraufwandes, um es bei Bedarf zur Verfügung zu haben.When an axial piston pump is used in an open circuit, cavitation difficulties arise in the area of the intake opening of the axial piston machine, unless care is taken to ensure that a satisfactory amount of the hydraulic medium to be drawn in is provided. To solve this problem, it is known to design the suction opening in the connection part of the axial piston pump to be larger than the discharge opening on the pressure side. With this configuration, the conveying direction of the axial piston machine is predetermined, and it is therefore not possible to change the conveying direction. In order to be able to use such an axial piston pump for both conveying directions, it has become common practice to provide two connecting parts configured in mirror image with respect to one another and corresponding control discs designed in mirror image with one another for the axial piston pump. By exchanging the connecting parts, such an axial piston pump can be adapted to the desired delivery direction. Such an embodiment is not only very complex, precisely because two connection parts are to be provided, but also requires storage effort with regard to the connection part not used in each case in order to have it available if required.

In dem Katalog: Mannesmann Rexroth "Mobil-Hydraulik-Komponenten" RD 64 001/11.86, Seiten 63 - 73 sind Pumpen nach dem Oberbegriff des Anspruches 1 beschrieben mit dem Hinweis, daß die Anschlußplatte bei Drehrichtung links um 180° gedreht ist. Über einen wahlweisen Einbau der Steuerscheibe in verschiedene Montagestellungen ist in dieser Schrift nichts ausgesagt. Aus der FR-A-2582738 ist eine ebenfalls dem Oberbegriff des Anspruches 1 entsprechende Axialkolbenpumpe beschrieben, bei der die Steuerscheibe durch einen Drehzapfen ersetzt ist, der zur Anpassung an unterschiedliche Förderrichtungen in unterschiedlichen Drehlagen einbaubar ist.In the catalog: Mannesmann Rexroth "Mobile Hydraulic Components" RE 64 001 / 11.86, pages 63 - 73 pumps according to the preamble of claim 1 are described with the indication that the connecting plate is rotated 180 ° to the left in the direction of rotation. Nothing is said in this document about an optional installation of the control disk in different mounting positions. FR-A-2582738 describes an axial piston pump which also corresponds to the preamble of claim 1 and in which the control disk is replaced by a pivot which can be installed in different rotational positions to adapt to different conveying directions.

Der Erfindung liegt die Aufgabe zugrunde, eine Axialkolbenpumpe der eingangs bezeichneten Art so auszugestalten, daß sie mit geringerem Aufwand an die jeweils andere Förderrichtung anpaßbar ist.The invention has for its object to design an axial piston pump of the type mentioned so that it can be adapted to the other direction of delivery with less effort.

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 läßt sich die Axialkolbenpumpe durch Drehen des aus Steuerscheibe und Anschlußteil bestehenden Steuerteils um 180° an die jeweils gewünschte Förderrichtung anpassen. Es bedarf somit keines zusätzlichen Anschlußteils und keiner zusätzlichen Steuerscheibe, wie es bei der bekannten Ausgestaltungen der Fall ist. Beim Verdrehen des Anschlußteils kommt es zwar zu einer Verlagerung der Ansaug- und Abgabeöffnungen bezüglich der Axialkolbenpumpe bzw. der sie aufnehmenden Maschine, jedoch läßt sich dieses Problem durch den Einsatz von flexiblen Anschlußleitungen oder passenden Anschlußleitungsabschnitten in einfacher Weise lösen. Die Erfindung ermöglicht die Anpaßbarkeit auch solcher Axialkolbenpumpen, deren Steuerscheiben hinsichtlich der Steueröffnungen (Steuernieren) in ansich bekannter Weise unsymmetrisch ausgebildet sind oder in ansich bekannter Weise sogenannte Druckausgleichskanäle aufweisen.In the embodiment according to the invention, the axial piston pump can be adjusted by rotating the control part consisting of the control disk and the connecting part through 180 ° to the desired delivery direction. There is therefore no need for an additional connecting part or an additional control disk, as is the case with the known configurations. When the connection part is rotated, there is a displacement of the suction and discharge openings with respect to the axial piston pump or the machine receiving it, however, this problem can be solved in a simple manner by using flexible connecting lines or suitable connecting line sections. The invention also makes it possible to adapt such axial piston pumps, the control disks of which are designed asymmetrically with respect to the control openings (control kidneys) or have so-called pressure compensation channels in a manner known per se.

Das Umrüsten der erfindungsgemäßen Axialkolbenpumpe ist deshalb sehr einfach, weil es lediglich einer Lösung und Entfernung der vorhandenen Befestigungsschrauben für das Anschlußteil bedarf. Danach läßt sich das Anschlußteil und die Steuerscheibe in einfacher Weise um 180° drehen, wobei ein vorteilhafterweise vorhandener im Querschnitt runder Zentrieransatz zwischen dem Anschlußteil und dem Gehäuse der Axialkolbenpumpe als Drehlager dienen kann.The retrofitting of the axial piston pump according to the invention is very simple because it only requires a solution and removal of the existing fastening screws for the connecting part. The connecting part and the control disk can then be rotated in a simple manner by 180 °, an advantageously existing centering projection with a round cross section between the connecting part and the housing of the axial piston pump serving as a rotary bearing.

Die erfindungsgemäße Ausgestaltung eignet sich für solche Axialkolbenpumpen, bei denen die Wechsel der Förderrichtung durch Änderung der Drehrichtung der Antriebswelle oder bei Axialkolbenpumpen verstellbarer Fördermenge durch eine Verstellung der Verstelleinrichtung über den Nullpunkt hinaus erfolgt.The configuration according to the invention is suitable for those axial piston pumps in which the delivery direction is changed by changing the direction of rotation of the drive shaft or, in the case of axial piston pumps, adjustable delivery rate by adjusting the adjusting device beyond the zero point.

Gemäß der Ausbildung nach Anspruch 4, wird eine einfache und praktische Kanalführung zur Beaufschlagung der Verstellvorrichtung der Axialkolbenpumpe vorgeschlagen, die in beiden Montagestellungen des Anschlußteils funktionsfähig und vorteilhaft ist.According to the embodiment of claim 4, a simple and practical channel guide for loading the adjusting device of the axial piston pump is proposed, which is functional and advantageous in both mounting positions of the connecting part.

Die Ausgestaltungen nach den Ansprüchen 5 und 6 beziehen sich auf eine integrierte hydraulische Verstellvorrichtung für eine Axialkolbenpumpe kleiner bzw. kompakter und auch einfacher Bauweise auch hinsichtlich betreffender Einzelteile.The configurations according to claims 5 and 6 relate to an integrated hydraulic adjustment device for an axial piston pump of small or compact and also simple construction also with regard to the individual parts concerned.

Bei einer Ausbildung gemäß Anspruch 9 erfolgt das Ausschwenken der Schiefscheibe durch die Triebwerkskräfte der Axialkolbenpumpe, so daß es keines zusätzlichen Ausschwenkmechanismus bedarf. Außerdem ist die Schiefscheibe einfach und leicht montierbar bzw. demontierbar. Dabei gewährleisten die Merkmale des Anspruchs 10 eine einfache und kostengünstige Herstellung, wobei die Lagerkörper aus fertigen Kugeln durch Nacharbeit wie Drehen hergestellt werden können.In a configuration according to claim 9, the swash plate is pivoted out by the engine forces of the axial piston pump, so that no additional pivoting mechanism is required. In addition, the swash plate is simple and easy to assemble or disassemble. The features of claim 10 ensure simple and inexpensive manufacture, the bearing bodies being able to be produced from finished balls by reworking such as turning.

Die Ansprüche 11 und 12 beziehen sich auf mechanische Anschläge, insbesondere zur Verhinderung des Überschwingens der Schwenkscheibe beim Einschwenken mit hohen Stellgeschwindigkeiten.Claims 11 and 12 relate to mechanical stops, in particular to prevent the swivel plate from overshooting when swiveling in at high positioning speeds.

Bei der Ausgestaltung gemäß Anspruch 13 wird die jeweils höher belastete Lagerstelle von der Gleitbahn der Schiefscheibe ausgehend, intermitierend und von der Höhe des Betriebsdruckes abhängig durch die Kolben mit Drucköl versorgt und somit vorteilhaft geschmiert Diese Ausgestaltung ermöglicht einen reibungsarmen und verschleißarmen Betrieb mit schnellen Stellzeiten.In the embodiment according to claim 13, the bearing that is more heavily loaded is starting from the slideway of the swash plate, intermittent and from the height of the operating pressure is supplied with pressure oil by the pistons and is therefore advantageously lubricated. This design enables low-friction and low-wear operation with fast operating times.

Nachfolgend wird die Erfindung anhand von in einer Zeichnung dargestellten bevorzugten Ausführungsbeispielen näher erläutert Es zeigt :

  • Fig. 1 eine erfindungsgemäß ausgestaltete Axialkolbenpumpe der Schiefscheibenbauart im axialen Schnitt;
  • Fig. 2 die Axialkolbenpumpe in der Unteransicht;
  • Fig. 3 eine Steuerscheibe der Axialkolbenpumpe in der Draufsicht ;
  • Fig. 4 den Schnitt IV-IV in Fig. 3 ;
  • Fig. 5 die Anschlußplatte der Axialkolbenpumpe in der Draufsicht.
The invention is explained in more detail below on the basis of preferred exemplary embodiments illustrated in a drawing.
  • 1 shows an axial piston pump designed according to the invention of the swash plate type in axial section;
  • Figure 2 shows the axial piston pump in the bottom view.
  • 3 shows a control disk of the axial piston pump in a top view;
  • Figure 4 shows the section IV-IV in Fig. 3.
  • Fig. 5, the connection plate of the axial piston pump in plan view.

Die in Fig. 1 allgemein mit 1 bezeichnete Axialkolbenpumpe weist ein zweiteiliges, aus einem topfförmigen Gehäuseteil 2 und einer Anschlußplatte 3 bestehendes Gehäuse auf, in dem eine sich längs der Mittelachse 4 erstreckende Antriebswelle 5 in Wälzlagern 6, 7 gelagert ist, von denen das eine dem topfförmigen Gehäuseteil 2 und das andere der Anschlußplatte 3 zugeordnet ist Auf der Antriebswelle 5 ist auf einem mit 8 bezeichneten Vielkeilabschnitt eine Zylindertrommel 9 gelagert, die auf einem Teilkreis gleichmäßig verteilt eine Mehrzahl Zylinderbohrungen 11 aufweist, in denen Kolben 12 aufgenommen sind. Die Kolben 12 weisen Kugelköpfe 13 auf, die in Gleitschuhe 14 einfassen, die an der Gleitfläche 15 einer Schiefscheibe 16 anliegen. Die Anlage an der Gleitfläche 15 wird durch eine Rückzugplatte 17 aufrechterhalten, die beim vorliegenden Ausführungsbeispiel mit einer kugelabschnittförmigen Ausnehmung 18 auf einem kugelkopfförmigen Trägerstück 19 gelagert ist. Das Trägerstück 19 ist längs verschieblich auf der Antriebswelle 5 gelagert.The axial piston pump, generally designated 1 in FIG. 1, has a two-part one made of a cup-shaped one Housing part 2 and a connection plate 3 existing housing in which a drive shaft 5 extending along the central axis 4 is mounted in roller bearings 6, 7, one of which is assigned to the cup-shaped housing part 2 and the other of the connection plate 3 is on the drive shaft 5 on a multi-wedge section denoted by 8, a cylinder drum 9 is mounted, which has a plurality of cylinder bores 11, evenly distributed on a pitch circle, in which pistons 12 are received. The pistons 12 have ball heads 13 which engage in sliding shoes 14 which bear against the sliding surface 15 of a swash plate 16. The contact with the sliding surface 15 is maintained by a retraction plate 17 which, in the present exemplary embodiment, is mounted on a spherical head-shaped carrier piece 19 with a recess 18 in the form of a spherical segment. The carrier piece 19 is mounted on the drive shaft 5 so as to be longitudinally displaceable.

Die Schiefscheibe 16 ist um eine Schwenkachse 22 in einem Schwenklager gelagert, das durch zwei längs der Schwenkachse 22 hintereinander liegende, allgemein mit 23 bezeichnete Auflager gebildet ist, bestehend aus zwei pilzkopfförmigen Lagerstücken 24, die mit ihren im Querschnitt runden Zapfen 25 in Bohrungen 26 im Boden des topfförmigen Gehäuseteils 2 eingesetzt sind und in sphärische Ausnehmungen 27 auf der Rückseite der Schiefscheibe 16 einfassen. Die den Kolben zugewandten sphärischen konvexen Flächen der Lagerstücke 24 und die sphärischen konkaven Flächen der Ausnehmungen 27 bilden somit gehäuseseitige und schiefscheibenseitige Lagerflächen 28. Beim vorliegenden Ausführungsbeispiel sind in den Ausnehmungen 27 pfannenförmige Lagerschalen 29 eingesetzt, die jeweils mit einem radial vorspringenden Kragen 31 am Umfangsrand der Ausnehmungen 27 anliegen und somit gegen Kippbewegungen gesichert sind.The swash plate 16 is mounted about a swivel axis 22 in a swivel bearing which is formed by two supports, generally designated 23, lying one behind the other along the swivel axis 22, consisting of two mushroom-shaped bearing pieces 24 which, with their round cross-section pin 25 in bores 26 in Bottom of the cup-shaped housing part 2 are inserted and surround in spherical recesses 27 on the back of the swash plate 16. The spherical convex surfaces of the bearing pieces 24 facing the pistons and the spherical concave surfaces of the recesses 27 thus form housing-side and swashplate-side bearing surfaces 28. In the present exemplary embodiment, pan-shaped bearing shells 29 are used in the recesses 27, each with a radially projecting collar 31 on the peripheral edge of the Recesses 27 abut and are thus secured against tilting movements.

Die Schwenkachse 22 der Schiefscheibe 16 befindet sich in einem Abstand a von der Wirklinie der aus den Kräften derwirksamen Kolben 12 resultierenden Kolbenkraft 32, wobei dieser Abstand a sich über die Mittelachse 4 hinaus erstreckt. Die resultierende Kolbenkraft 32 wird von den sich auf der jeweiligen Druckseite befindlichen Kolben 12 erzeugt. Aufgrund des Abstands a wird im Betrieb der Axialkolbenpumpe 1 die Schiefscheibe 16 mit einem Drehmoment gemäß Fig. 1 entgegen Uhrzeigersinn belastet Hierdurch ist die Anlage der Schiefscheibe 16 an ihre Verstellung bewirkenden hydraulischen Stellkolben 33 gewährleistet, die parallel zur Antriebswelle 5 im Boden- bzw. Flanschteil des topfförmigen Gehäuseteils 2 angeordnet und in Zylinderbohrungen 34 achsparallel zur Antriebswelle 5, d.h. in Richtung des Doppelpfeils 35 hydraulisch verschiebbar sind. Die Verstellkolben 33 sind der wirksamen resultierenden Kolbenkraft 32 gegenüberliegend angeordnet, d.h. sie befinden sich bezüglich der Schwenkachse 22 auf der anderen Seite der Axialkolbenpumpe 1, wobei sie einen gleichen Abstand von der Mittelachse 4 aufweisen, ziemlich nahe beieinander und symmetrisch zu einer rechtwinklig zur Schwenkachse 22 verlaufenden Querachse 36 angeordnet sind, vgl. Fig. 2. In der dargestellten Position gemäß Fig. 1 befindet sich die Schiefscheibe 16 in ihrer Position maximalen Kolbenhubs. Durch ein Ausfahren der Stellkolben 33 kann die Schiefscheibe 16 um die Schwenkachse 22 in wahlweise Schwenkstellungen bzw. Fördermengeneinstellungen verstellt werden. Zur Begrenzung der maximalen Schwenkstellung sind Anschläge 37 zu beiden Seiten der axialen Querebene 36 den Stellkolben 33 etwa gegenüberliegend angeordnet, die durch seitlich von außen in das Gehäuseteil 2 eingesetzte Bolzen oder Schrauben 38 mit Anschlagzapfen gebildet sind. Bei Anlage an den Anschlägen 37 ist die Axialkolbenmaschine 1 auf minimalen Kolbenhub und minimale Fördermenge eingestellt.The pivot axis 22 of the swash plate 16 is located at a distance a from the line of action of the piston force 32 resulting from the forces of the active pistons 12, this distance a extending beyond the central axis 4. The resulting piston force 32 is generated by the pistons 12 located on the respective pressure side. Due to the distance a, the swash plate 16 is loaded counterclockwise with a torque according to FIG of the cup-shaped housing part 2 arranged and in cylinder bores 34 axially parallel to the drive shaft 5, ie are hydraulically displaceable in the direction of the double arrow 35. The adjusting pistons 33 are arranged opposite the effective resulting piston force 32, i.e. they are located on the other side of the axial piston pump 1 with respect to the pivot axis 22, being at an equal distance from the central axis 4, arranged fairly close to one another and symmetrical to a transverse axis 36 running at right angles to the pivot axis 22, cf. Fig. 2. In the position shown in FIG. 1, the swash plate 16 is in its maximum piston stroke position. By extending the actuating piston 33, the swash plate 16 can be adjusted about the pivot axis 22 in either pivot positions or delivery quantity settings. To limit the maximum pivoting position, stops 37 are arranged on both sides of the axial transverse plane 36 approximately opposite the actuating pistons 33, which are formed by bolts or screws 38 with stop pins inserted laterally into the housing part 2 from the outside. When bearing against the stops 37, the axial piston machine 1 is set to a minimum piston stroke and a minimum delivery rate.

Die Schwenklager 23 sind durch jeweils einen von der Ausnehmung 27 ausgehenden und die Lagerschale 29 sowie die Schiefscheibe 16 durchquerenden Schmierkanal 39 mit dem ölführenden System der Axialkolbenmaschine 1 verbunden und somit ölgeschmiert. Beim vorliegenden Ausführungsbeispiel mündet der Schmierkanal 39 in der Gleitfläche 15 der Schiefscheibe 16 in der Nähe des Teilkreises, auf dem die Kolben 12 angeordnet sind und zwar in einem Bereich, den die Gleitschuhe 14 mit einer Ausnehmung 41 in deren Gleitfläche 42 bestreichen. Die Ausnehmung 41 steht mittels ansich bekannten axialen Kanälen 43, 44 in den Gleitschuhen 14 und den Kolben 12 mit den Arbeitsräumen 45 der Kolbenzylinder in Verbindung. Auf diese Weise wird im Betrieb der Axialkolbenpumpe 1 die jeweils höher belastete Lagerstelle des Schwenklagers 23 beim Überstreichen der Gleitschuhe 14 intermitierend mit unter Arbeitsdruck stehendem Schmieröl versorgt.The pivot bearings 23 are each connected to the oil-carrying system of the axial piston machine 1 by a lubrication channel 39 which extends from the recess 27 and crosses the bearing shell 29 and the swash plate 16 and is thus oil-lubricated. In the present exemplary embodiment, the lubrication channel 39 opens into the sliding surface 15 of the swash plate 16 in the vicinity of the pitch circle on which the pistons 12 are arranged, specifically in an area which the sliding shoes 14 cover with a recess 41 in their sliding surface 42. The recess 41 is connected to the working spaces 45 of the piston cylinders by means of axially known channels 43, 44 in the sliding shoes 14 and the pistons 12. In this way, when the axial piston pump 1 is in operation, the bearing point of the pivot bearing 23 which is subjected to higher loads is intermittently supplied with lubricating oil under working pressure when the sliding shoes 14 are swept over.

Die Zylindertrommel 9 liegt mit ihrer der Schiefscheibe 16 abgewandten Stimseite an einer Steuerplatte 46 an, die zwischen der Zylindertrommel 9 und der Anschlußplatte 3 angeordnet und um die Mittelachse 4 drehfest an derAnschlußplatte 3 gehalten ist. Die in Fig. 3 im einzelnen dargestellte Steuerplatte 46 weist zwei im wesentlichen nierenförmige, sie durchsetzende Steueröffnungen 47, 48 auf, an die sich in der Anschlußplatte 3 ebenfalls nierenförmige Saug- bzw. Druckkanäle 51, 52 anschließen, von denen der Saugkanal 51 einen gegenüber dem Druckkanal 52 im Querschnitt vergrößerten Endquerschnitt, nämlich eine große Ansaugöffnung 53, hier ein Anschluß für eine nicht dargestellte Ansaugleitung, aufweist. Beim vorliegenden Ausführungsbeispiel ist die Steuerniere 48 auf der Druckseite durch Verstärkungsstege 50 unterbrochen.The cylinder drum 9 lies with its end facing away from the swashplate 16 against a control plate 46 which is arranged between the cylinder drum 9 and the connection plate 3 and is held on the connection plate 3 in a rotationally fixed manner about the central axis 4. The control plate 46 shown in detail in FIG. 3 has two essentially kidney-shaped control openings 47, 48 penetrating it, to which kidney-shaped suction or pressure channels 51, 52 also adjoin in the connecting plate 3, of which the suction channel 51 is opposite the pressure channel 52 with an enlarged end cross section, namely a large suction opening 53, here a connection for a suction line, not shown. In the present exemplary embodiment, the control kidney 48 is interrupted on the pressure side by reinforcing webs 50.

An den Enden der Steuernieren 47,48, die der jeweiligen und in Fig. 3 beispielhaft durch den Pfeil 54 dargestellten Drehrichtung entgegengesetzt sind, sind ansich bekannte Druckausgleichskerben 55,56 angeordnet, deren Zweck es ist, die schlagartige Wirkung der Druckveränderungen in den Arbeitsräumen 45 zu verringern, wenn die in der Zylindertrommel 9 vorhandenen, von den Arbeitsräumen 45 ausgehenden Steuerkanäle 57 mit der Hochdruck- oder Niederdruck enthaltenden Steuerniere 47,48 in Verbindung gelangen.Known pressure compensation notches 55, 56 are arranged at the ends of the control kidneys 47, 48, which are opposite to the respective direction of rotation, which is exemplified by the arrow 54 in FIG. 3, the purpose of which is to improve the sudden effect of the pressure changes in the working spaces 45 to be reduced if the control channels 57 which are present in the cylinder drum 9 and extend from the working spaces 45 come into contact with the control kidneys 47, 48 containing high or low pressure.

Beim vorliegenden Ausführungsbeispiel weist die Steuerplatte 46 auf beiden Seiten Druckausgleichskerben 56 auf und zwar an ein und demselben Ende wenigstens der Hochdruck-Steuerniere 48. D.h., auf der Rückseite der Steuerplatte 46 gemäß Fig. 3 sind ebenfalls Druckausgleichskerben 55,56 hinter den sichtbaren Druckausgleichskerben 55,56 vorhanden. Die Druckausgleichskerben 55,56 gehen vom betreffenden Ende der Steuerniere 47,48 aus und konvergieren keilförmig, wie es im Teilschnitt gemäß Fig. 4 dargestellt ist.Die Druckausgleichskerbe(n) 55 sind ggf. auf beiden Seiten der Steuerplatte 46, vorzugsweise am der Drehrichtung 54 entgegengesetzten Ende der Niederdruck-Steuerniere 47 angeordnet.In the present exemplary embodiment, the control plate 46 has pressure compensation notches 56 on both sides, namely at one and the same end of at least the high-pressure control kidney 48. That is, on the rear of the control plate 46 according to FIG. 3 there are also pressure compensation notches 55, 56 behind the visible pressure compensation notches 55 , 56 available. The pressure compensation notches 55, 56 extend from the relevant end of the control kidneys 47, 48 and converge in a wedge shape, as shown in the partial section according to FIG. 4. The pressure compensation notches (s) 55 are optionally on both sides of the control plate 46, preferably in the direction of rotation 54 opposite end of the low-pressure control kidney 47 arranged.

Die Drehsicherung der Steuerplatte 46 erfolgt duch eine Zapfenverbindung mit einem vorzugsweise von der Anschlußplatte 3 ausgehenden Zapfen 60 (Fig. 5), der in ein Sackloch oder Durchgangsloch 61 in der Steuerplatte 46 einfaßt.The control plate 46 is secured against rotation by means of a pin connection with a pin 60 (FIG. 5) which preferably extends from the connecting plate 3 and which fits into a blind hole or through-hole 61 in the control plate 46.

Die Anordnung ist so getroffen, daß die Steuerplatte 46 wahlweise mit ihrer einen oder anderen Stirnseite an die Anschlußplatte 3 angesetzt werden kann und zwar ist sie im wesentlichen um eine mit der Querachse 36 gemäß Fig. 2 parallelen Querachse 58 klappbar, so daß die Steuernieren 47, 48 immer mit den ebenfalls nierenförmigen Saug- bzw. Druckkanälen 51, 52 in derAnschlußplatte 3 korrespondieren. Dabei ist vorzugsweise die Anordnung des Zapfens 60 und eines den Zapfen 60 jeweils aufnehmenden, hier durchgehenden Zapfenlochs 61 so getroffen, daß die beiden wahlweisen Montagepositionen der Steuerplatte 46 sich bezüglich der durch die Anschlußplatte 3 vorgegebene Position unterscheiden, und zwar ist die eine Montageposition gegenüber der anderen Montageposition in Umfangsrichtung versetzt, was durch den in Fig. 4 dargestellten, einen Versatz des Zapfenlochs 61 zur Querachse 58 darstellenden Winkel b verdeutlicht ist. D.h., die Steuernieren 47, 48 liegen bezüglich der durch die Steuerkanäle 57 vorgegebenen Anordnung nicht symmetrisch und zwar aus funktionellen Gründen zwecks Erreichung eines bestimmten Vorlaufs, was ansich bekannt ist Der Winkel b1 in Fig. 3 zeigt den Winkelversatz in der umgeklappten Montagestellung der Steuerplatte 46.The arrangement is such that the control plate 46 can optionally be attached with its one or the other end face to the connection plate 3, namely it can be folded essentially about a transverse axis 58 parallel to the transverse axis 36 according to FIG. 2, so that the control kidneys 47 , 48 always correspond to the likewise kidney-shaped suction or pressure channels 51, 52 in the connection plate 3. In this case, the arrangement of the pin 60 and a pin hole 61 which receives the pin 60 and passes through here is preferably such that the two optional mounting positions of the control plate 46 differ with respect to the position predetermined by the connecting plate 3, namely that one mounting position is opposite the one another mounting position offset in the circumferential direction, which is illustrated by the angle b shown in FIG. 4, which represents an offset of the pin hole 61 to the transverse axis 58. That is, the control kidneys 47, 48 are not symmetrical with respect to the arrangement predetermined by the control channels 57, namely for functional reasons in order to achieve a certain advance, which is known per se. The angle b 1 in FIG. 3 shows the angular offset in the folded mounting position of the control plate 46.

Beim vorliegenden Ausführungsbeispiel ist die Steuerplatte 46 parallel ausgestaltet.In the present exemplary embodiment, the control plate 46 is configured in parallel.

Im Betrieb wird die Zylindertrommel 9 durch die Antriebswelle 5 in Rotation versetzt. Dabei geraten die Zylinderbohrungen 11 über die Steuerkanäle 57 wechselseitig mit den Steuernieren 47, 48 in Verbindung, wodurch aufgrund der Bewegung der Kolben 12 die Pumpwirkung sich in bekannter Weise ergibt. Die Strömungsrichtung des hydraulischen Mediums ist in Fig. 1 durch die Pfeile 62 und 63 verdeutlicht Die Abdichtung zwischen der Zylindertrommel 9 und der Steuerplatte 46 ist durch eine Druckfeder 64 gewährleistet, die zwischen einem Innenring 65 der Zylindertrommel 9 und einem Druckring eingespannt ist. Zwischen dem Druckring und dem Trägerstück 19 erstrecken sich wenigstens ein axiales Druckelement beim vorliegenden Ausführungsbeispiel in Form von drei auf dem Umfang verteilten Druckstiften 66, die in einer Führung der Zylindertrommel 9 axial verschiebbar sind. Durch die Druckfeder 64 werden somit die Zylindertrommel 9 gegen die Steuerplatte 46 und das Trägerstück 19 gegen die Rückzugplatte 17 und folglich auch die Schiefscheibe 16 gegen das Auflager 23 elastisch beaufschlagt. Ein vergleichbarer Zweck könnte in vorteilhafter Weise auch durch z.B. in den Zylinderbohrungen 11 angeordneten Druckfedern erreicht werden, die die Kolben 12 in Richtung auf die Schiefscheibe 16 beaufschlagen.In operation, the cylinder drum 9 is rotated by the drive shaft 5. The cylinder bores 11 are mutually connected to the control kidneys 47, 48 via the control channels 57, as a result of which the pumping action results in a known manner due to the movement of the pistons 12. The direction of flow of the hydraulic medium is illustrated in FIG. 1 by arrows 62 and 63. The seal between the cylinder drum 9 and the control plate 46 is ensured by a compression spring 64 which is clamped between an inner ring 65 of the cylinder drum 9 and a pressure ring. At least one axial pressure element in the present exemplary embodiment extends in the form of three pressure pins 66 distributed around the circumference, which are axially displaceable in a guide of the cylinder drum 9, between the pressure ring and the carrier piece 19. By means of the compression spring 64, the cylinder drum 9 is thus elastically acted against the control plate 46 and the carrier piece 19 against the retraction plate 17 and consequently also the swash plate 16 against the support 23. A comparable purpose could also advantageously be achieved by e.g. compression springs arranged in the cylinder bores 11 are applied, which act on the pistons 12 in the direction of the swash plate 16.

Die Anschlußplatte 3 ist so ausgestaltet, daß sie um die Mittelachse 4 wahlweise um 180° verdreht montierbar ist. Dies gilt insbesondere für die beim vorliegenden Ausführungsbeispiel vier Stück auf einem Teilkreis gleichmäßig verteilten Befestigungsschrauben 67 und die sich auf die Steueranordnung beziehenden Ausgestaltungen wie die nierenförmigen Saug- bzw. Druckkanalabschnitte 51, 52, die Zapfenverbindung zwischen der Anschlußplatte 3 sowie der Steuerplatte 46 und der allgemein mit 68 bezeichneten Zentrierung mit einem im Querschnitt runden Ansatz 69 an der Anschlußplatte 3, der etwa schließend in den im Querschnitt ebenfalls runden Hohlraum 71 des Gehäuses einfaßt. Die Anschlußplatte 3 kann somit nach Lösen und Entfernen der Befestigungsschrauen 67 um 180° gedreht und wieder befestigt werden. Durch ein gleichzeitiges Umklappen der Steuerplatte 46 in die andere bzw. richtige Funktionsstellung läßt sich die Axialkolbenmaschine 1 in einfacher Weise an eine Umkehrung der Förderrichtung anpassen und zwar läßt sich die im Querschnitt größere Ansaugöffnung 53 in die durch die Umkehrung der Strömungsrichtung vorgegebene Position anordnen, nämlich wahlweise auf der einen oder anderen Seite der Axialkolbenmaschine 1, so daß ein störungsfreies Ansaugen bzw. eine störungsfreie Füllung der ansaugenden Kolbenzylinder erreicht wird.The connection plate 3 is designed such that it can be mounted rotated by 180 ° about the central axis 4. This applies in particular to the four fastening screws 67 evenly distributed on a pitch circle in the present exemplary embodiment and the configurations relating to the control arrangement such as the kidney-shaped suction or pressure channel sections 51, 52, the pin connection between the connection plate 3 and the control plate 46 and the general with 68 designated centering with a round in cross-section 69 on the connecting plate 3, which roughly surrounds the cavity 71 of the housing, which is also round in cross-section. The connection plate 3 can thus be rotated and loosened after loosening and removing the fastening screws 67 by 180 °. By simultaneously flipping the control plate 46 into the other or correct functional position, the axial piston machine 1 can be adapted in a simple manner to a reversal of the conveying direction, and indeed the larger suction opening 53 in cross section can be arranged in the position predetermined by the reversal of the flow direction, namely optionally on one or the other side of the axial piston machine 1, so that trouble-free suction or trouble-free filling of the suction piston cylinders is achieved.

Beim vorliegenden Ausführungsbeispiel ist die Anschlußplatte 3 aus gezogenem Profilmaterial vorzugsweise quadratischen Querschnitts hergestellt. Hierdurch ist eine kostengünstige Herstellung möglich. Die Befestigungsschrauben 67 sind in einander gegenüberliegender Position in den Eckenbereich der Anschlußplatte 3 angeordnet.In the present embodiment, the connection plate 3 is made of drawn profile material, preferably a square cross-section. This enables cost-effective production. The fastening screws 67 are arranged in an opposite position in the corner region of the connection plate 3.

Die Montage bzw. Demontage der Schiefscheibe 16 ist sehr einfach, weil sie nach entfernung der Anschlußplatte 3 sowohl einzeln als auch auf der Antriebswelle 5 als Baueinheit vormontiert von der offenen Seite des Gehäuses her in das Gehäuseteil 2 eingesetzt und in entgegengesetzter Richtung wieder entnommen werden kann.The assembly or disassembly of the swash plate 16 is very simple because after removing the Connection plate 3 both individually and on the drive shaft 5 as a pre-assembled unit inserted into the housing part 2 from the open side of the housing and can be removed again in the opposite direction.

Beim vorliegenden Ausführungsbeispiel ist zur Fördermengeneinstellung der Axialkolbenpumpe 1 ein allgemein mit 72 bezeichnetes Ventil vorgesehen, mit dem es möglich ist, die Fördermengeneinstellung in Abhängigkeit des vorhandenen Arbeitsdruckes so zu regeln, daß mit steigendem Arbeitsdruck die Fördermenge verringert und mit sinkendem Arbeitsdruck die Fördermenge vergrößert wird (Druckregelung) oder die Fördermenge auch nur druckabhängig begrenzt wird.In the present exemplary embodiment, a valve, generally designated 72, is provided for adjusting the delivery rate of the axial piston pump 1, with which it is possible to regulate the delivery rate setting as a function of the existing working pressure in such a way that the delivery rate decreases with increasing working pressure and the delivery rate increases with decreasing working pressure ( Pressure control) or the delivery rate is only limited depending on the pressure.

Hierzu ist das Ventil 72 in einer den Druckkanal 52 mit den Arbeitsräumen 73 der allgemein mit 74 bezeichneten Verstellzylinder verbindenden Leitung angeordnet, um die Beaufschlagung der Verstellkolben 33 zu regeln oder zu steuern. Dieser aus mehreren Abschnitten und mit 75 bezeichnete Verbindungskanal ist im Bereich der Anschlußplatte 3 mit dem Druckkanal 52 verbunden. Um auch bei den vorhandenen beiden um 180° zueinander verdrehten Anbaupositionen der Anschlußplatte 3 die hydraulische Versorgung der Verstellzylinder 74 bzw. die Abnahme des Arbeitsdruckes zu gewährleisten, sind in der Anschlußplatte 3 zwei von außen angebohrte und verschlossene Verbindungskanalzweige 76, 77 (Fig. 5) vorgesehen, von denen der eine Verbindungskanalzweig 76 in der einen Montageposition und der andere Verbindungskanalzweig 77 in der um 180° verdrehten anderen Montageposition der Anschlußplatte 3 an der mit 78 bezeichneten Schnittstelle (Fig. 1) des Verbindungskanals 75 korrespondiert. Diese Schnittstelle 78 befindet sich in der Teilungsfuge zwischen dem Gehäuseteil 2 und der Anschlußplatte 3, und sie ist in nicht dargestellter Weise zur Teilungsfuge hin abgedichtet.For this purpose, the valve 72 is arranged in a line connecting the pressure channel 52 with the working spaces 73 of the adjusting cylinders, generally designated 74, in order to regulate or control the action on the adjusting pistons 33. This connecting channel, which consists of several sections and is designated by 75, is connected to the pressure channel 52 in the region of the connecting plate 3. In order to ensure the hydraulic supply of the adjusting cylinders 74 and the decrease of the working pressure even with the existing two mounting positions of the connecting plate 3 rotated relative to one another, two connecting channel branches 76, 77 drilled and closed from the outside are in the connecting plate 3 (FIG. 5). provided, of which the one connecting channel branch 76 corresponds in one assembly position and the other connecting channel branch 77 in the other mounting position of the connecting plate 3 rotated by 180 ° at the interface designated 78 (FIG. 1) of the connecting channel 75. This interface 78 is located in the parting line between the housing part 2 and the connecting plate 3, and it is sealed off from the parting line in a manner not shown.

Von dieser Schnittstelle 78 aus verläuft der Verbindungskanal 75 zunächst axial im Gehäuseteil 2 in den Bereich des daran seitlich und vorzugsweise symmetrisch an einer Anbaufläche 79 angesetzten und in nicht dargestellter Weise befestigten Ventils 72, dessen Ventilgehäuse allgemein mit 81 bezeichnet ist. Beim vorliegenden Ausführungsbeispiel weist das Ventil 72 einen Ventilschieber 82 mit einem zu beiden Seiten Steuerkanten aufweisenden Bund auf, der mit einem von der den Schieber 82 aufnehmenden Bohrung 86 zu den Arbeitsräumen 73 erstreckenden Verbindungskanalabschnitt 87 eine variable Ventilöffnung bildet. Der Schieber 82 ist an seinem in Fig. 1 oberen Ende durch eine Feder 89 in eine die Ventilöffnung schließende Stellung beaufschlagt. Beim Vorhandensein eines bzw. eines bestimmten Arbeitsdrucks wird der Schieber 82 entgegen der Feder 89 hochgedrückt, wodurch der Durchgang am Verbindungskanalabschnitt 87 geöffnet und die Verstellkolben 33 über Verbindungskanalzweige 91,92 (Fig. 2) zwecks Verringerung bzw. Begrenzung der Fördermenge hydraulisch ausgefahren werden. Die Verbindungskanalabschnitte 91,92 sind jeweils über eine Umfangsnut 93 und einen radialen und axialen Verbindungskanalabschnitt 94,95 (Fig. 1) im Verstellkolben 33 mit den Arbeitsräumen 73 der Verstellzylinder 74 verbunden.From this interface 78, the connecting channel 75 initially runs axially in the housing part 2 in the region of the valve 72, which is attached laterally and preferably symmetrically to an attachment surface 79 and is fastened in a manner not shown, the valve housing of which is generally designated 81. In the present exemplary embodiment, the valve 72 has a valve slide 82 with a collar which has control edges on both sides and which forms a variable valve opening with a connecting channel section 87 extending from the bore 86 receiving the slide 82 to the working spaces 73. The slide 82 is urged at its upper end in FIG. 1 by a spring 89 into a position closing the valve opening. If a or a certain working pressure is present, the slide 82 is pushed up against the spring 89, as a result of which the passage on the connecting channel section 87 is opened and the adjusting piston 33 are hydraulically extended via connecting channel branches 91, 92 (FIG. 2) in order to reduce or limit the delivery rate. The connecting duct sections 91, 92 are each connected to the working spaces 73 of the adjusting cylinders 74 via a circumferential groove 93 and a radial and axial connecting duct section 94.95 (FIG. 1) in the adjusting piston 33.

Die Entlüftung der Verstellzylinder 74 und des die Feder 89 sowie ein Druckstück 96 aufnehmenden Hohlraums 97 ist durch Entlüftungskanalabschnitte 98,99,100 gewährleistet, die mit dem Gehäuse-Hohlraum 71 des Pumpengehäuses verbunden sind. Beim vorliegenden Ausführungsbeispiel wird der Entlüftungskanalabschnitt 98 vom hinter dem Bund liegenden Bohrungsabschnitt 86 gebildet, d.h. dieser Entlüftungskanalabschnitt 98 geht von der Ventilöffnung aus, und er ist bei einer Beaufschlagung der Verstellkolben 33 durch den Bund verschlossen.The venting of the adjusting cylinders 74 and of the cavity 97 receiving the spring 89 and a pressure piece 96 is ensured by venting channel sections 98, 99, 100, which are connected to the housing cavity 71 of the pump housing. In the present exemplary embodiment, the ventilation duct section 98 is formed by the bore section 86 lying behind the collar, i.e. this ventilation duct section 98 starts from the valve opening and is closed when the adjusting piston 33 is acted upon by the collar.

Die Vorspannkraft der Feder 89 ist durch eine Stellschraube 101 einstellbar, an die die Feder 89 sich über einen Federsteller 102 abstützt. Die Stellschraube 101 ist durch eine Mutter 103 sicherbar.The biasing force of the spring 89 can be adjusted by means of an adjusting screw 101, against which the spring 89 is supported via a spring actuator 102. The adjusting screw 101 can be secured by a nut 103.

Es ist im Rahmen der Erfindung möglich, das Ventil 72 so auszugestalten und die Anordnung so zu treffen, daß es die Schiefscheibe 16 zwischen lediglich zwei Stellungen, nämlich zwischen der Maximal- und Minimaleinstellung, zu verstellen vermag.It is possible within the scope of the invention to design the valve 72 and to arrange it in such a way that it can adjust the swash plate 16 between only two positions, namely between the maximum and minimum settings.

Es ist zu bemerken, daß die im Querschnitt größere Ansaugöffnung 53, die im Querschnitt kleinere Abgabeöffnung 104, die Ansaugund Druckkanäle 51,52 und die Steuernieren 47,48 in Fig. 1 zwecks Verbesserung des Verständnisses um 90° verdreht dargestellt sind, was durch eine Bruchlinie verdeutlicht ist. In Wirklichkeit liegen die vorgenannten Ausgestaltungsmerkmale zu beiden Seiten der Querebene 36 (siehe Fig. 5), die auch die Schnittebene gemäß Fig. 1 darstellt, und in der auch die Querachse 58 liegt.It should be noted that the larger suction opening 53, the smaller discharge opening 104, the suction and Pressure channels 51, 52 and the control kidneys 47, 48 in FIG. 1 are shown rotated by 90 ° in order to improve understanding, which is illustrated by a broken line. In reality, the aforementioned design features lie on both sides of the transverse plane 36 (see FIG. 5), which also represents the sectional plane according to FIG. 1, and in which the transverse axis 58 also lies.

Beim Ausführungsbeispiel gemäß Fig. 1 wird die Umkehrung der Förderrichtung durch Drehrichtungswechsel der Antriebswelle 5 erreicht. Eine Förderrichtungsumkehrung kann jedoch auch dadurch erreicht werden, daß die vorhandene Verstellvorrichtung der Axialkolbenpumpe im Gegensatz zum Ausführungsbeispiel gemäß Fig. 1 über den Nullpunkt hinaus verstellbar ist.In the exemplary embodiment according to FIG. 1, the reversal of the conveying direction is achieved by changing the direction of rotation of the drive shaft 5. However, a reversal of the conveying direction can also be achieved in that the existing adjusting device of the axial piston pump, in contrast to the exemplary embodiment according to FIG. 1, can be adjusted beyond the zero point.

Claims (13)

  1. An axial piston pump of fixed or adjustable displacement, in particular of the swash plate type, having a two-part housing, namely a housing part accommodating the pistons either directly or indirectly and a connecting piece through which the pressure passage and the suction passage extend, wherein the suction passage has a suction opening larger in cross-section than the pressure passage, the pistons are arranged in a rotatable cylinder drum and a control disc having control openings is arranged between the cylinder drum and the connecting piece, characterised in that the control disc (46) can be mounted as desired in two mounting positions which, in relation to one another, are turned substantially through 180° about the centre axis (4) of the axial piston pump (1) and are turned about a transverse axis (58) extending substantially centrally of the control openings (47, 48), and in that the connecting piece (3) can be mounted on the housing part (82) in two alternative positions which, in relation to one another, are turned substantially through 180° about the centre axis (4) of the axial piston pump (1).
  2. An axial piston pump according to claim 1, characterised in that the control openings (47, 48) in the control disc (46) are slightly offset (angle b1) in the circumferential direction relative to the transverse axis (58).
  3. An axial piston machine according to claim 1 or claim 2, characterised in that the control disc (46) has pressure balancing passages (55, 56) on both front faces at the ends opposite the direction of rotation (54) of the axial piston pump (1).
  4. An axial piston pump according to any preceding claim, characterised in that the swash plate (16) can be adjusted by an adjusting cylinder (74) which is connected to the pressure passage (52) within the connecting piece (3) by a connecting passage (75) extending through the housing part (2) and the connecting piece (3), wherein the connecting passage (75) has, in the region of the connecting piece (3), two connecting passage sections (76, 77), of which the one connecting passage branch (76) in one mounting position and the other connecting passage branch (77) in the other mounting position of the connecting piece (3) corresponds in the joint (78) with the section of the connecting passage extending in the housing part (2).
  5. An axial piston pump according to claim 4, characterised in that the adjusting cylinder (74) is integrated in the flange or floor of the housing part (2).
  6. An axial piston pump according to claim 4 or 5, characterised in that two adjusting cylinders (74) are provided of which the adjusting pistons (33) are arranged next to one another on an imaginary pitch circle.
  7. An axial piston pump according to any of claims 4 to 6, characterised in that the at least one adjusting cylinder (74) can be controlled or regulated by a control or regulating valve (72) acted on by the working pressure.
  8. An axial piston pump according to claim 7, characterised in that the control or regulating valve (72) is arranged laterally on the housing part (2), opposite the adjusting cylinder (74), in particular in a position symmetrical with respect to two adjusting cylinders (74) present.
  9. An axial piston pump according to any of claims 1 to 8, characterised in that the swash plate (16) is arranged on two bearing parts (24) spaced apart and having free spherical bearing surfaces (28) facing the pistons, loosely between the bearing parts (24) and the pistons (12), wherein the swivel axis (22) extending through the bearing parts (24) is at a distance (a) from the corresponding direction of force (32) of the pistons (12) and the at least one adjusting piston (33) presses loosely against the side of the swash plate (16) remote from the pistons (12).
  10. An axial piston pump according to claim 9, characterised in that the bearing parts (24) are mushroom-shaped and are inserted with their stems (25) in holes (26) in the housing part (2) or parts built thereon.
  11. An axial piston pump according to any of claims 4 to 10, characterised in that the maximum tilting position of the swash plate (16) is limited by the adjusting piston (33) being pushed right up against a stop.
  12. An axial piston pump according to any of claims 4 to 11, characterised in that associated with the swash plate (16) on the side on which the at least one adjusting cylinder (74) is arranged, is at least one stop (37) to limit its minimum tilt position which is preferably formed by a screw (38) screwed from the outside into the housing part (2).
  13. An axial piston pump according to any of claims 9 to 12, characterised in that the heads of the pistons (12) are pivotably mounted in slippers (13) which abut against the drive disc (16), in that a respective lubricating passage is provided which extends from the recess (27) through the swash plate (16) and emerges at its inclined surface (15), and which corresponds with lubricating passages which extend longitudinally through the pistons (12) and the slippers (13).
EP88120650A 1987-12-18 1988-12-09 Axial piston pump Expired - Lifetime EP0320822B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873743125 DE3743125A1 (en) 1987-12-18 1987-12-18 AXIAL PISTON PUMP
DE3743125 1987-12-18

Publications (3)

Publication Number Publication Date
EP0320822A1 EP0320822A1 (en) 1989-06-21
EP0320822B1 EP0320822B1 (en) 1991-03-06
EP0320822B2 true EP0320822B2 (en) 1997-01-29

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ID=6343006

Family Applications (1)

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EP88120650A Expired - Lifetime EP0320822B2 (en) 1987-12-18 1988-12-09 Axial piston pump

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US (1) US4934253A (en)
EP (1) EP0320822B2 (en)
JP (1) JP2554927B2 (en)
DE (2) DE3743125A1 (en)

Families Citing this family (63)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2500892Y2 (en) * 1989-08-31 1996-06-12 帝人製機株式会社 Adjustable hydraulic actuator
JP2559632B2 (en) * 1989-11-22 1996-12-04 株式会社小松製作所 Swash plate angle changing device for swash plate type piston pump / motor
DE3942189C1 (en) * 1989-12-20 1991-09-05 Hydromatik Gmbh, 7915 Elchingen, De
DE4229007C2 (en) * 1992-08-31 2002-06-13 Linde Ag Axial piston machine in swash plate design
DE4301121C2 (en) * 1993-01-18 1995-03-30 Danfoss As Hydraulic axial piston machine with a swash plate
US5423560A (en) * 1994-03-17 1995-06-13 Warrick; John J. Variable speed hydraulic drive, for single or multi-wheel drive bicycles and the like
WO1996001947A1 (en) * 1994-07-08 1996-01-25 Danfoss A/S A piston with a slide shoe and method of manufacturing same
JP3179296B2 (en) * 1994-08-11 2001-06-25 株式会社ゼクセルヴァレオクライメートコントロール Hinge ball of variable displacement rocking plate compressor
DE19503617C2 (en) * 1995-02-03 1999-06-02 Sauer Sundstrand Gmbh & Co Pressure fluid unit with variable stroke volume
DE19521574A1 (en) * 1995-06-14 1996-12-19 Rexroth Mannesmann Gmbh Hydrostatic pump or motor with cylindrical drum
KR100298021B1 (en) * 1996-10-08 2002-04-06 세구치 류이치 Manufacturing method of swash plate hydraulic rotor and casing for two rotor
DE19643389C1 (en) * 1996-10-21 1998-01-02 Brueninghaus Hydromatik Gmbh Axial piston machine with adjustable control plate
SE514196C2 (en) * 1997-12-08 2001-01-22 Parker Hannifin Ab Hydraulic rotary axial piston machine
SE521484C2 (en) 1998-02-13 2003-11-04 Parker Hannifin Ab Hydraulic rotary axial piston machine
SE514384C2 (en) 1998-04-17 2001-02-19 Parker Hannifin Ab Hydraulic rotary axial piston machine
US6027250A (en) * 1998-08-21 2000-02-22 The Torrington Company Roller bearing segment for swashplates and other limited-oscillation applications
US6358018B1 (en) 1999-02-12 2002-03-19 Parker Hannifin Ab Hydraulic rotating axial piston engine
US6889595B1 (en) 1999-07-16 2005-05-10 Hydro-Gear Limited Partnership Pump
US6694729B1 (en) 1999-07-16 2004-02-24 Hydro-Gear Limited Partnership Pump
US6332393B1 (en) 1999-07-16 2001-12-25 Hydro-Gear Limited Partnership Pump
US7178336B1 (en) 1999-07-16 2007-02-20 Hydro-Gear Limited Partnership Pump
US7082762B1 (en) 1999-07-16 2006-08-01 Hydro-Gear Limited Partnership Pump
US6354809B1 (en) 2000-01-27 2002-03-12 Ford Global Technologies, Inc. Variable swash plate compressor
US6210124B1 (en) 2000-01-27 2001-04-03 Ford Global Technologies, Inc. Variable swash plate compressor
DE10044784B4 (en) * 2000-09-11 2006-03-23 Sauer-Danfoss (Neumünster) GmbH & Co OHG Schrägachsenverstelleinheit
US6494686B1 (en) 2000-10-30 2002-12-17 Hydro-Gear Limited Partnership Tandem pump and interface for same
US6793463B1 (en) 2000-10-30 2004-09-21 Hydro-Gear Limited Partnership Tandem pump and interface for same
US6629822B2 (en) 2000-11-10 2003-10-07 Parker Hannifin Corporation Internally supercharged axial piston pump
US6675696B1 (en) * 2001-12-14 2004-01-13 Hydro-Gear Limited Partnership Pump and center section for hydrostatic transmission
US6672843B1 (en) 2002-04-08 2004-01-06 Hydro-Gear Limited Partnership Dual pump apparatus comprising dual drive shafts and auxiliary pump
US20040175277A1 (en) * 2002-06-28 2004-09-09 Cox C. Paul Hydrostatic pump assembly having symmetrical endcap
TW565652B (en) * 2002-12-13 2003-12-11 Ind Tech Res Inst Stirling engine with variable stroke
EP1435457A1 (en) * 2003-01-03 2004-07-07 Lavorwash S.p.A. Swash plate pump with automatically variable flow rate
US6953327B1 (en) 2003-03-11 2005-10-11 Hydro-Gear Limited Partnership Dual pump
JP2007524026A (en) * 2003-06-18 2007-08-23 トーマス　インダストリーズ　インコーポレーテツド Hybrid perturbation pump
US7278263B1 (en) 2003-06-27 2007-10-09 Hydro-Gear Limited Partnership Charge pump for a hydraulic pump
US7007468B1 (en) 2003-06-27 2006-03-07 Hydro-Gear Limited Partnership Charge pump for a hydrostatic transmission
JP4425590B2 (en) * 2003-09-09 2010-03-03 株式会社 神崎高級工機製作所 Pumping unit
DE102004007933B3 (en) * 2004-02-18 2005-06-16 Sauer-Danfoss (Neumünster) GmbH & Co OHG Axial piston engine and associated control system to dampen peak gas flow impulses by an inertia regulation passage
US7040638B2 (en) * 2004-06-21 2006-05-09 Jeffrey Eaton Cole Occupant-propelled fluid powered rotary device, truck, wheeled platform, or vehicle
US7216876B2 (en) * 2004-06-21 2007-05-15 Cole Jeffrey E Occupant-propelled fluid powered rotary device, truck, wheeled platform, or vehicle
WO2006002205A2 (en) 2004-06-21 2006-01-05 Cole Jeffrey E Truck assembly for a skateboard, wheeled platform, or vehicle
US7232139B2 (en) * 2004-06-21 2007-06-19 Cole Jeffrey E Truck assembly for a skateboard, wheeled platform, or vehicle
US7789846B2 (en) * 2005-01-25 2010-09-07 Thermopeutix, Inc. System and methods for selective thermal treatment
US7635136B2 (en) * 2005-06-21 2009-12-22 Jeffrey E. Cole Truck assembly for a skateboard, wheeled platform, or vehicle
EP1780410B1 (en) * 2005-10-26 2013-04-03 Poclain Hydraulics Variable displacement hydraulic machine having a swash plate
US7451687B2 (en) * 2005-12-07 2008-11-18 Thomas Industries, Inc. Hybrid nutating pump
US7726126B1 (en) 2005-12-21 2010-06-01 Hydro-Gear Limited Partnership Dual pump apparatus with power take off
US7257948B1 (en) 2005-12-21 2007-08-21 Hydro-Gear Limited Partnership Dual pump apparatus
DE102007024174B4 (en) * 2006-12-11 2022-09-08 Robert Bosch Gmbh Axial piston machine with an anti-twist device for the control plate
WO2008116136A1 (en) * 2007-03-21 2008-09-25 Gardner Denver Thomas, Inc. Hybrid nutating pump with anti-rotation feature
US7806040B2 (en) * 2007-09-12 2010-10-05 Sauer-Danfoss Inc. Ball supported swashplate for axial piston hydraulic machine
JP4934749B1 (en) * 2011-02-23 2012-05-16 株式会社小松製作所 Variable displacement hydraulic pump / motor
US9103339B2 (en) 2011-02-28 2015-08-11 James H. Gammon Piston pump
CA2913062C (en) 2013-05-22 2020-06-02 Hydac Drive Center Gmbh Axial piston pump having a swash-plate type construction
DE102013211450A1 (en) * 2013-06-19 2014-12-24 Robert Bosch Gmbh Axial piston machine with a lubrication hole for the actuator piston
CN103486016A (en) * 2013-09-16 2014-01-01 同济大学 Valve plate for low-noise anti-cavitation plunger pump
US20160252080A1 (en) * 2013-12-18 2016-09-01 Schaeffler Technologies AG & Co. KG Variable displacement pump
DE102015212731A1 (en) 2015-07-08 2017-01-12 Robert Bosch Gmbh Housing for a hydrostatic axial piston machine and hydrostatic axial piston machine with a housing
CH712152A1 (en) * 2016-02-25 2017-08-31 Liebherr Machines Bulle Sa Axial piston machine, in particular axial piston pump.
DE102017206901A1 (en) 2017-04-25 2018-10-25 Robert Bosch Gmbh Hydrostatic axial piston machine
DE102018205884A1 (en) * 2018-04-18 2019-10-24 Robert Bosch Gmbh Axial piston machine with pressure relief in the Durchtriebsraum
US11236736B2 (en) * 2019-09-27 2022-02-01 Honeywell International Inc. Axial piston pump with port plate having balance feed aperture relief feature

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR15964E (en) * 1910-12-08 1912-10-26 Louis Brun Reversible rotary motor
DE1098780B (en) * 1955-12-02 1961-02-02 Daimler Benz Ag Control of the supply and discharge of operating fluid in a hydrostatic axial piston transmission
GB1069671A (en) * 1963-06-19 1967-05-24 Lucas Industries Ltd Hydraulic reciprocating pumps and motors
US3585901A (en) * 1969-02-19 1971-06-22 Sundstrand Corp Hydraulic pump
DE1939297A1 (en) * 1969-08-01 1971-02-11 Linde Ag Axial piston machine
FR2082604A5 (en) * 1970-03-20 1971-12-10 Boyer Jean
DE2208890A1 (en) * 1972-02-25 1973-09-06 Bosch Gmbh Robert AXIAL PISTON PUMP
US4034652A (en) * 1975-03-06 1977-07-12 Caterpillar Tractor Co. Method and valve face configuration for reducing noise in a hydraulic pump
FR2476762A2 (en) * 1980-02-22 1981-08-28 Leduc & Fils Rene HYDRAULIC PUMP WITH BIAIS TRAY THAT CAN TURN IN BOTH WAYS
DE3233579C2 (en) * 1982-09-10 1984-09-13 Hermann Hemscheidt Maschinenfabrik Gmbh & Co, 5600 Wuppertal Axial piston machine
US4550645A (en) * 1984-04-27 1985-11-05 Sundstrand Corporation Thin valve plate for a hydraulic unit
FR2582738B1 (en) * 1985-05-31 1989-06-30 Leduc Rene Hydro Sa HYDRAULIC AXIAL PISTON MACHINE WITH CENTRAL AND FLOATING DISTRIBUTOR THAT CAN OPERATE EITHER ENGINE, EITHER PUMP

Also Published As

Publication number Publication date
JP2554927B2 (en) 1996-11-20
DE3743125A1 (en) 1989-07-06
JPH01200068A (en) 1989-08-11
DE3861956D1 (en) 1991-04-11
EP0320822A1 (en) 1989-06-21
US4934253A (en) 1990-06-19
EP0320822B1 (en) 1991-03-06

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