EP1278960B1 - Hydrostatic machine - Google Patents

Hydrostatic machine Download PDF

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Publication number
EP1278960B1
EP1278960B1 EP01905687A EP01905687A EP1278960B1 EP 1278960 B1 EP1278960 B1 EP 1278960B1 EP 01905687 A EP01905687 A EP 01905687A EP 01905687 A EP01905687 A EP 01905687A EP 1278960 B1 EP1278960 B1 EP 1278960B1
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EP
European Patent Office
Prior art keywords
hydrostatic
housing body
machine according
bodies
add
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.)
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Application number
EP01905687A
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German (de)
French (fr)
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EP1278960A1 (en
Inventor
Günter Wanschura
Reinhold Schniederjan
Jürgen GINTNER
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Brueninghaus Hydromatik GmbH
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Brueninghaus Hydromatik GmbH
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Publication of EP1278960A1 publication Critical patent/EP1278960A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—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 stationary cylinders
    • F04B1/16—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 stationary cylinders having two or more sets of cylinders or pistons

Definitions

  • the invention relates to a hydrostatic machine according to the preamble of claim 1.
  • this known hydrostatic machine is a so-called double pump unit with a one-piece main housing body, which has a centrally disposed housing middle wall and on each side a housing end wall, in each case between the housing middle wall and the housing end walls a housing chamber is arranged, in each of which a cylinder drum is arranged with substantially axially reciprocally guided piston guided therein, which are supported on a likewise arranged in the housing chamber pivoting body.
  • the cylinder drums are each mounted on a drive shaft, which are rotatably mounted on the inside in bearing bores of the housing middle wall and on the outside pass through the associated housing end wall in a bearing hole and are also rotatably mounted therein.
  • Each swivel body is associated with an adjusting device with a reciprocable adjusting element, which is also displaceably mounted in the one-piece main housing body back and forth.
  • the two drive shafts of the first and second hydrostatic unit thus formed are rotatably connected to each other in the region of the housing middle wall by a sleeve-shaped coupling piece.
  • the housing chambers each have an access opening arranged transversely to the associated drive shaft, by means of which the associated pivot body can be mounted or removed.
  • the access openings are each closed by a cover plate on which bearing surfaces for a Swivel bearings of the associated pivot body are formed.
  • On the side opposite the cover plates bearing surfaces for the swivel bodies are arranged on the one-piece main housing body. While the one housing end wall serves as a mounting flange for the hydrostatic machine, an auxiliary pump is attached to the other housing end wall, which is driven by the associated drive shaft, which projects into the auxiliary pump body.
  • the main housing body is not only of a complicated design due to the additional presence of the transverse access openings, but it is also considerably weakened by the access openings, so that the main housing body must be made stable in its remaining sections in order to those in functional operation sold to him To be able to absorb loads.
  • Another disadvantage is the fact that two additional cover plates are to be provided, whereby not only the number of components is increased, but also to assemble and seal and contribute to the complicated design.
  • the pivot bearing for the swivel body are each partially formed on the main housing body and partially on the associated cover plate.
  • the invention has for its object to simplify a hydrostatic machine of the type specified while ensuring a stable construction.
  • a first attachment housing body mounted on the main housing body is provided on which the pivot body of the first hydrostatic unit is mounted and a second attachment housing body adjoining the main housing body is provided on which the pivot body of the second hydrostatic unit is mounted.
  • the first and the second mounting housing body form end-side mounting parts, which are arranged in the region of the front housing openings anyway required for the passage of the drive shafts, in the area while ensuring a simple design, a stable attachment of the mounting housing body to the main housing body is possible.
  • the front-side openings can be formed so large that the cylinder drum and the swivel body of the first and second hydrostatic unit are each mounted by the frontal openings or can be disassembled.
  • a significant advantage of the embodiment according to the invention can also be seen in that the pivot bearings are each realized on one and the same component, namely on the first and second mounting housing bodies.
  • the respective bearing surfaces of the pivot bearing can be precisely manufactured on the attachment housing bodies not only in a simple manner and easily accessible but also in a clamping on a processing machine, whereby the quality of storage improves and the life of the pivot bearing is extended.
  • Another advantage of the embodiment of the invention is that at the first and second Attachment housing body is formed both the pivot bearing and the bearing for the associated drive shaft, whereby not only a compact design but also a simple and accurate production of both bearing configurations is achieved in each case one and the same attachment housing body.
  • the housing of the hydrostatic machine consists only of three components, namely the one-piece main housing body and the two attachment housing bodies.
  • the mounting housing body can be formed as components that are rotatable after solving associated fasteners, in particular fastening screws, about the axis of rotation of the associated drive shaft and are mountable in different rotational positions of the main housing body. This is particularly advantageous if the hydrostatic units are formed by axial piston machines. By attaching the attachment housing body in angled by 180 ° mounting positions can namely determine the direction of rotation of the interconnected drive shafts. This improves the operational capability of the hydrostatic machine and its adaptation to different operating conditions.
  • the drive shafts can each form a mounting unit with the associated mounting housing body, if both mounting units are mirror-symmetrical with respect to a perpendicular to the drive shaft axes extending center plane of the main housing body.
  • Such a configuration makes it possible to mount the hydrostatic units rotated by 180 ° with respect to a transverse axis extending in the median plane. This not only ensures that the output end of the drive shaft assembly can be arranged either on one side or on the other, but it is also possible in the above sense, the direction of rotation of the hydraulic unit to certain.
  • the main parts of the hydrostatic machine designated in its entirety by 1 are a main housing body 2, two attached to these at opposite end faces mounting housing body 3a, 3b, two housing chambers 4a, 4b, in each of which a hydrostatic unit E1, E2, preferably in the form of a piston machine 5a, 5b, is arranged, wherein the piston machines 5a, 5b are each adjustable by an adjusting device 6a, 6b with respect to their throughput volume.
  • the piston machines 5a, 5b each have a drive shaft 7a, 7b, which are arranged coaxially, wherein the mutually facing drive shaft ends are rotatably supported by bearings 8a, 8b on a housing middle wall 9, which extends between the housing chambers 4a, 4b.
  • the opposite ends of the drive shaft 7a, 7b are mounted by means of pivot bearings 11a, 11b on the mounting housing bodies 3a, 3b, which have through holes in which the pivot bearings 11a, 11b are arranged.
  • a channel 9a connecting the chambers 4a, 4b is provided in the housing middle wall 9, preferably in the region of the side on which the adjusting devices 6a, 6b are arranged.
  • the piston machines 5a, 5b each have a cylinder drum 13a, 13b, in which approximately axially parallel and circumferentially distributed piston holes piston 14a, 14b are mounted reciprocally displaceable, which arranged by at their outwardly facing ends spherical joints 15 with in sliding shoes 16 pivotally mounted spherical piston heads on a swash plate 17a, 17b are axially supported on a pivot body 17c with arranged on both sides of the drive shaft 7a, 7b pivot skids of a pivot bearing 18a, 18b with circular arc-shaped convex bearing surfaces 19a on corresponding arcuate concave bearing surfaces 19b the inner sides of the mounting housing body 3a, 3b are pivotable about pivot axes 22a, 22b, each extending at right angles to the axes of rotation 21 of the drive shafts 7a, 7b.
  • the pivoting or adjusting devices 6a, 6b provided for this purpose are each formed by a hydraulic piston cylinder, which are connected by a connecting joint 23 to a swivel arm 24a, 24b protruding inwardly from the swivel body 17c.
  • the piston cylinders extend transversely to the axis of rotation 21, wherein they are located in lateral chamber extensions of the housing chamber 4a, 4b and are mounted correspondingly displaceable in the main housing body 2.
  • the swash plates 17a, 17b surround the associated drive shaft 7a, 7b annularly.
  • the cylinder drums 13a, 13b are respectively non-rotatably connected to the associated drive shaft 7a, 7b, and they rest with their inwardly facing end faces in each case on a control disk 25a, 25b with control openings which extend through in the housing middle wall 9 supply channels 26a, 26b and discharge channels 27a, 27b are not shown in Fig. 1, arranged on the main housing body 2 inlets and outlets for a hydraulic medium, in particular hydraulic oil, are connected.
  • the mutually facing ends of the drive shafts 7a, 7b are preferably connected to each other in a rotationally fixed manner.
  • a coupling 28, z. B. in the form of a coupling sleeve 28 a serve, which engages over the two drive shaft ends sleeve-shaped and z. B. by arranged on the lateral surface of the drive shaft ends and on the inner circumferential surface of the coupling sleeve 28a, interlocking teeth are positively connected with each other.
  • the coupling sleeve 28a has a radial distance from the inner wall of the existing bearing hole in the housing middle wall 9.
  • the outer teeth on the drive shaft ends and preferably also the inner teeth on the coupling sleeve 28a or their tooth flanks are preferably curved convexly around the drive shaft ends transversely traversing axes.
  • the attachment housing body 3a, 3b each have a radial body wall 3c, on the inner sides of the bearing surfaces 19 are formed for the pivot body 17c.
  • the body walls 3c can be mounted and sealed directly on frontal mounting surfaces 29 on the main housing body 2.
  • the mounting housing body 3a, 3b formed with the body walls 3c in each case inwardly projecting peripheral walls 3e pot-shaped, wherein the peripheral walls 3d abut with their frontal Anbauzan 31 on the cultivation surfaces 29 and sealed.
  • For sealing is preferably a sealing ring 33, for. B. O-ring, provided, which is associated with the centering surfaces 32 in an outer ring groove or inner ring groove in a conventional manner.
  • the hydrostatic machine 1 with respect to a between the piston machines 5a, 5b in the region of the housing center wall 9 perpendicular to the common axis of rotation 21 extending center plane E mirror image that the reciprocating engines 5a, 5b preferably with the associated mounting housing bodies 3a, 3b in order 180 ° rotated positions on the main housing body 2 can be mounted.
  • This is particularly advantageous when the attachment housing body 3a, 3b at their sides facing the main housing body 2 equal, but are formed differently on their sides facing away from each other. In this case, given by the different design of the mounting housing body 3a, 3b predetermined different mounting situations can be created either on one side or on the other side of the main housing body 2.
  • the present embodiment is used by the drive shaft journal 7c of the drive shaft 7a interspersed, here left, mounting housing body 3a with an annular stepped mounting surface 34 the cultivation of the hydrostatic machine 1 to a support, not shown.
  • the other attachment housing body 3b can serve for the cultivation of at least one further unit or a further hydraulic unit E3, z. B. an auxiliary pump, which is not shown in Fig. 1.
  • the fastening means effective between the attachment housing bodies 3a, 3b and the main housing body 2 in such a way that the attachment housing bodies 3a, 3b can be optionally mounted on the main housing body 2 in positions rotated 180 ° about the rotation axis 180 and with the associated adjustment device Ga, Gb are connectable.
  • the direction of rotation of the reciprocating machines 5 a, 5 b can be reversed and adapted to existing requirements at the installation site.
  • the attachment housing body 3b facing away from the drive pin 7c carries a third hydraulic unit E3 or an additional unit, here in the form of an auxiliary pump 35, which is driven by an extended drive pin 7d of the associated drive shaft 7b. It is z.
  • a gear pump with at least one feed gear 35 which is mounted directly on the drive pin 7 d or rotatably seated on a sleeve 36 which is rotatably connected to the drive pin 7 d.
  • the radial body wall 3c is widened, wherein in it preferably at the periphery of an inlet 37 and an outlet 38 are arranged, of which each connecting channels 39, 41 extend to the pressure and low pressure zone of the gear pump.
  • the conveyor gear 35 is located in a chamber of a mounting plate 42 which is mounted on the front side of the body wall 3c and thereby preferably in a recess in the body wall 3c and centered therein is.
  • the housing 2b of the third hydrostatic unit E3 is designated by 2b.
  • the drive pin 7c oppositely disposed mounting housing body 3b is also preferably a one-piece part of a third hydraulic unit E3, preferably by a piston machine 5c, in particular an axial piston machine , is formed.
  • the piston engine 5c may be constant or adjustable with regard to its throughput volume. It can be a swashplate machine whose cylindrical drum 13c is mounted non-rotatably on a drive shaft extension 45 which is in particular one-piece.
  • the drive shaft extension 45 can in a conventional manner, the cylinder drum 13c and arranged on the outer end face cam 46 axially pass through in receiving holes and be stored with a bearing pin 45a by means of a pivot bearing 47 on a lid 48, which may be part of a fourth hydraulic unit E4 can, which may be an auxiliary pump with a housing 2c.
  • the lid 48 and the body of the auxiliary pump is tightly attached to an integrally extending from the body wall 3 c peripheral wall 49, z. B. screwed surrounding a third working chamber 51, in which the third hydraulic unit E3 is arranged in a conventional manner.
  • the swash plate 17c of the swash plate machine 5c is supported on the radial body wall 3c.
  • the drive shaft extension 45 may be a separate drive shaft, the inner drive shaft end is rotatably supported by a pivot bearing 53 in a bearing hole of the radial body wall 3c.
  • two pivot bearings 11b, 53 can be arranged axially next to one another, as shown in FIG.
  • the hydraulic supply lines and channels for the piston engine 5c are of a known type and for reasons of simplicity not described in detail. If the drive shaft 54 for the third piston engine 43 is a separate drive shaft, its drive shaft end can be positively connected to the opposite drive shaft end of the drive shaft 7b, z. B. positively by a clutch 28, as has already been described in the embodiment of FIG. 1. When the auxiliary pump can be such. B. is a gear pump, which is described in the embodiment of FIG. 1.
  • the axially outer bearing pin 54 of the additional drive shaft or the drive shaft extension 45 end face by a coupling pin 55 coaxially extended, which engages positively in a coupling sleeve 56, z. B. in the sense of a toothed or multi-tooth clutch, wherein the coupling sleeve 56 may be driving part of the auxiliary pump.
  • the pivot bearing 18 of the second hydrostatic unit E2 is also arranged on Anbaugekorusegroper 3b, which is part of the housing 2b of the third hydrostatic unit E3, preferably also by a piston machine 5c, in particular an axial piston machine, is formed.
  • the piston engine 5c is preferably adjustable in terms of its throughput volume, which may be a swash plate machine, the swash plate 17c is pivotally mounted.
  • the pivoting plane of the associated pivot bearing 18c is arranged rotated by 90 ° with respect to the adjacent or second pivot bearing 18b and also with respect to the first pivot bearing 18a, as shown in FIG. 5.
  • the pivot bearing 18 c may also have the same pivoting plane.
  • the associated adjusting device 6c may be such a automotive adjusting device 6c, which reduces the throughput volume with increasing working pressure and increases the throughput volume with decreasing working pressure.
  • the swash plate 17c can be adjusted by a spring in its maximum pivot position, with the increasing working pressure, the swash plate 17c is adjusted against the force of the spring in the direction of their minimum volume setting.
  • the spring 58 is formed by a compression spring disposed on the pressure side of the swash plate 17c between it and the body wall 3c.
  • the peripheral wall 49 of the housing 2b is closed in this embodiment by a voltage applied to its edge cover 48, on which the pivot bearing 47 is supported for the associated drive shaft.
  • This drive shaft may be a drive shaft extension or a separate drive shaft, as has already been described.
  • Fig. 6 shows the embodiment of FIG. 5 in a rotated by 90 ° partial section view.
  • FIG. 7 wherein the same or similar parts are provided with the same reference numerals, based on the embodiment of FIG. 3, but with a common pivot bearing 61 for the outer drive shaft end of the drive shaft 7b and the inner drive shaft end of a separate drive shaft 7c of third hydrostatic unit E3 is provided.
  • the common pivot bearing 61 is formed by the fact that the outer end of the drive shaft 7b and the inner end of the drive shaft 7c cooperate coaxially sleeve-shaped, wherein the cross-part is rotatably mounted in a bearing of the body wall 3c.
  • a common roller bearing 52 is provided, which sits on the overarching part.
  • This is preferably formed by the fact that the outer end of the drive shaft 7b with a coaxial, in particular hollow cylindrical recess 63 as a bearing sleeve 64 is formed, in which the correspondingly shaped inner end of the drive shaft 7c is seated and rotatably connected, for. B. by a single or multi-part connection or a screw thread.
  • FIG. 8 differs from the embodiment of FIG. 7 in that the common pivot bearing 61 is formed by a separate bearing sleeve 64 a, in the from both end sides the drive shafts 7b, 7c are firmly inserted with appropriately adapted bearing journals, z. B. by a wedge or screw.
  • the trunnions can bear directly against each other with their free ends or the drive shafts 7b, 7c can rest with shoulder surfaces on the front ends of the bearing sleeve 64 and thus be axially limited and positioned.
  • the rolling bearing 62 axially limiting shoulder surfaces of the bearing sleeve 64a are also provided.
  • the one shoulder surface is formed by a preferably integrally formed annular shoulder on the bearing sleeve 64, while the other shoulder surface is formed by a releasable locking ring which sits in an annular groove.
  • the roller bearing 62 can be mounted or dismounted from the side facing the main housing body 2. It lies with its side facing away from the main housing body 2 on a shoulder surface 65 in the housing 2b and in the body wall 3c.
  • a mounting housing body as shown in FIG. 1, the mounting housing body 3a, serve as mounting flange for the multiple hydraulic unit thus formed, the other attachment housing body 3b assumes the function of fürtriebsdorfkeit.
  • adjusting devices 6a, 6b are also advantageous to integrate the adjusting devices 6a, 6b in the main housing body 2 for the direct supply of the two adjusting devices 6a, 6b. This eliminates additional acreage on the main housing body 2, and also a small and compact and for the adjusting devices 6a, 6b protected construction is achieved. Furthermore, it is advantageous to provide only an internal tank connection and a supply pressure protection for the first and the second hydraulic unit E1, E2. This requires only a single tank connection. It is advantageous to arrange the feed in the center of the main housing body 2 in front of a feed pressure relief valve. The discharged via a pressure relief valve hydraulic medium is returned via the housing chambers 4a, 4b by means of an internal connection at the tank connection to the tank.
  • the drive shaft journal 7c surrounding or located in its vicinity front attachment housing body 3a can form a flange for mounting the complete multiple hydraulic unit while ensuring a stable construction and attachment.
  • the other or rear cultivation housing body 3b carries the drive shaft bearing and the swivel body bearing of the second hydraulic unit, and it can also support a molded housing with suction and pressure connections for a third hydraulic unit E3, z.
  • a gear machine or a piston machine form.
  • different drive-through variants can also be carried out. This allows a through drive adapter and the Anflanschschild the third hydraulic unit save on.
  • this embodiment leads to a significant reduction in length.
  • a clutch 28 between the drive shafts 7a, 7b or 7c each in the sense of a spatial joint allbeweglich, z. B. "spherical”, run to avoid unavoidable tolerances deflections of the drive shafts.

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

Description

Die Erfindung betrifft eine hydrostatische Maschine nach dem Oberbegriff des Anspruchs 1.The invention relates to a hydrostatic machine according to the preamble of claim 1.

Eine hydrostatische Maschine dieser Art ist in der DE 195 12 993 A1 (und DE-A-19 828 180) beschrieben.A hydrostatic machine of this type is described in DE 195 12 993 A1 (and DE-A-19 828 180).

Bei dieser bekannten hydrostatischen Maschine handelt es sich um ein sogenanntes Doppelpumpen-Aggregat mit einem einstückigen Hauptgehäusekörper, der eine mittig angeordnete Gehäusemittelwand und auf jeder Seite eine Gehäusestirnwand aufweist, wobei jeweils zwischen der Gehäusemittelwand und den Gehäusestirnwänden eine Gehäusekammer angeordnet ist, in der jeweils eine Zylindertrommel mit darin im wesentlichen axial hin und her verschiebbar geführten Kolben angeordnet ist, die sich an einem ebenfalls in der Gehäusekammer angeordneten Schwenkkörper abstützen. Die Zylindertrommeln sind jeweils auf einer Triebwelle gelagert, die innenseitig in Lagerbohrungen der Gehäusemittelwand drehbar gelagert sind und außenseitig die zugehörige Gehäusestirnwand in einem Lagerloch durchsetzen und darin ebenfalls drehbar gelagert sind. Jedem Schwenkkörper ist eine Verstellvorrichtung mit einem hin und her bewegbaren Verstellelement zugeordnet, das ebenfalls im einstückigen Hauptgehäusekörper hin und her verschiebbar gelagert ist. Die beiden Triebwellen der so gebildeten ersten und zweiten hydrostatischen Einheit sind im Bereich der Gehäusemittelwand durch ein muffenförmiges Kupplungsstück drehfest miteinander verbunden. Bei dieser bekannten hydrostatischen Maschine ist den Gehäusekammern jeweils eine quer zur zugehörigen Triebwelle angeordnete Zugangsöffnung zugeordnet, durch die der zugehörige Schwenkkörper montierbar bzw. demontierbar ist. Die Zugangsöffnungen sind jeweils durch eine Abdeckplatte verschließbar, an denen Lagerflächen für ein Schwenklager des zugehörigen Schwenkkörpers ausgebildet sind. Auf der den Abdeckplatten gegenüberliegenden Seite sind Lagerflächen für die Schwenkkörper am einstückigen Hauptgehäusekörper angeordnet. Während die eine Gehäusestirnwand als Anbauflansch für die hydrostatische Maschine dient, ist an die andere Gehäusestirnwand eine Hilfspumpe angebaut, die durch die zugehörige Triebwelle angetrieben wird, die in den Hilfspumpenkörper hineinragt.In this known hydrostatic machine is a so-called double pump unit with a one-piece main housing body, which has a centrally disposed housing middle wall and on each side a housing end wall, in each case between the housing middle wall and the housing end walls a housing chamber is arranged, in each of which a cylinder drum is arranged with substantially axially reciprocally guided piston guided therein, which are supported on a likewise arranged in the housing chamber pivoting body. The cylinder drums are each mounted on a drive shaft, which are rotatably mounted on the inside in bearing bores of the housing middle wall and on the outside pass through the associated housing end wall in a bearing hole and are also rotatably mounted therein. Each swivel body is associated with an adjusting device with a reciprocable adjusting element, which is also displaceably mounted in the one-piece main housing body back and forth. The two drive shafts of the first and second hydrostatic unit thus formed are rotatably connected to each other in the region of the housing middle wall by a sleeve-shaped coupling piece. In this known hydrostatic machine, the housing chambers each have an access opening arranged transversely to the associated drive shaft, by means of which the associated pivot body can be mounted or removed. The access openings are each closed by a cover plate on which bearing surfaces for a Swivel bearings of the associated pivot body are formed. On the side opposite the cover plates bearing surfaces for the swivel bodies are arranged on the one-piece main housing body. While the one housing end wall serves as a mounting flange for the hydrostatic machine, an auxiliary pump is attached to the other housing end wall, which is driven by the associated drive shaft, which projects into the auxiliary pump body.

Diese bekannte Ausgestaltung ist aus mehreren Gründen nachteilig. Zum einen ist der Hauptgehäusekörper durch das zusätzliche Vorhandensein der quer gerichteten Zugangsöffnungen nicht nur von einer komplizierten Bauform, sondern er wird durch die Zugangsöffnungen auch beträchtlich geschwächt, so daß der Hauptgehäusekörper in seinen übrigen Bauabschnitten stabil ausgebildet werden muß, um die im Funktionsbetrieb an ihn abgesetzten Belastungen aufnehmen zu können. Ein weiterer Nachteil ist darin zu erkennen, daß zwei zusätzliche Abdeckplatten vorzusehen sind, wodurch nicht nur die Anzahl der Bauteile vergrößert wird, sondern die auch zu montieren und abzudichten sind und zu der komplizierten Bauweise beitragen. Darüber hinaus sind bei dieser bekannten Ausgestaltung die Schwenklager für die Schwenkkörper jeweils teilweise am Hauptgehäusekörper und teilweise an der zugehörigen Abdeckplatte ausgebildet. Hierin ist ein weiterer Nachteil zu erkennen, da aufgrund kaum zu vermeidender Toleranzen mit Positionsunterschieden zwischen den am Hauptgehäusekörper angeordneten Lagerflächen und den an den Abdeckplatten angeordneten Lagerflächen zu rechnen ist, was zu einer Beeinträchtigung der Schwenklager für die Schwenkkörper führt, insbesondere bei hohen Belastungen, wodurch die Lebensdauer der Schwenklager und somit auch der hydrostatischen Maschine insgesamt beeinträchtigt werden kann.This known embodiment is disadvantageous for several reasons. On the one hand, the main housing body is not only of a complicated design due to the additional presence of the transverse access openings, but it is also considerably weakened by the access openings, so that the main housing body must be made stable in its remaining sections in order to those in functional operation sold to him To be able to absorb loads. Another disadvantage is the fact that two additional cover plates are to be provided, whereby not only the number of components is increased, but also to assemble and seal and contribute to the complicated design. In addition, in this known embodiment, the pivot bearing for the swivel body are each partially formed on the main housing body and partially on the associated cover plate. This is another disadvantage to recognize because due to hardly avoidable tolerances with position differences between the arranged on the main housing body bearing surfaces and arranged on the cover bearing surfaces is expected, which leads to an impairment of the pivot bearing for the swivel body, especially at high loads, thereby the life of the pivot bearing and thus the hydrostatic machine can be affected as a whole.

Der Erfindung liegt die Aufgabe zugrunde, eine hydrostatische Maschine der eingangs angegebenen Art bei Gewährleistung einer stabilen Bauweise zu vereinfachen.The invention has for its object to simplify a hydrostatic machine of the type specified while ensuring a stable construction.

Dabei soll nicht nur die Bauweise des einstückigen Hauptgehäusekörpers vereinfacht werden, sondern auch die Schwenklager für den Schwenkkörper, wobei ferner nicht nur eine einfache sondern auch eine präzise Herstellung der Schwenklager erreicht werden soll.In this case, not only the construction of the one-piece main housing body should be simplified, but also the pivot bearing for the swivel body, further not only a simple but also a precise production of the pivot bearing is to be achieved.

Diese Aufgabe wird durch die Merkmale des Anspruchs 1 gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen beschrieben.This object is solved by the features of claim 1. Advantageous developments of the invention are described in the subclaims.

Bei der erfindungsgemäßen hydrostatischen Maschine ist ein an den Hauptgehäusekörper montierter erster Anbaugehäusekörper vorgesehen, an dem der Schwenkkörper der ersten hydrostatischen Einheit gelagert ist, und es ist ein an dem Hauptgehäusekörper anschließender zweiter Anbaugehäusekörper vorgesehen, an dem der Schwenkkörper der zweiten hydrostatischen Einheit gelagert ist. Dabei bilden der erste und der zweite Anbaugehäusekörper stirnseitige Anbauteile, die im Bereich der für den Durchgang der Triebwellen ohnehin erforderlichen stirnseitigen Gehäuseöffnungen angeordnet sind, in deren Bereich bei Gewährleistung einer einfachen Ausgestaltung ein stabiler Anbau der Anbaugehäusekörper an den Hauptgehäusekörper möglich ist. Dabei können die stirnseitigen Öffnungen so groß ausgebildet werden, daß die Zylindertrommel und die Schwenkkörper der ersten und zweiten hydrostatischen Einheit jeweils durch die stirnseitigen Öffnungen montier- bzw. demontierbar sind. Ein wesentlicher Vorteil der erfindungsgemäßen Ausgestaltung ist auch darin zu erkennen, daß die Schwenklager jeweils an ein und demselben Bauteil, nämlich an den ersten und zweiten Anbaugehäusekörpern realisiert sind. Dabei können die betreffenden Lagerflächen der Schwenklager an den Anbaugehäusekörpern jeweils nicht nur in einfacher Weise und bequem zugänglich sondern auch in einer Aufspannung an einer Bearbeitungsmaschine präzise hergestellt werden, wodurch die Qualität der Lagerung verbessert und die Lebensdauer des Schwenklagers verlängert wird. Ein weiterer Vorteil der erfindungsgemäßen Ausgestaltung besteht darin, daß am ersten und am zweiten Anbaugehäusekörper sowohl das Schwenklager als auch das Lager für die zugehörige Triebwelle ausgebildet ist, wodurch nicht nur eine kompakte Bauweise sondern ebenfalls auch eine einfache und präzise Herstellung beider Lagerausbildungen an jeweils ein und demselben Anbaugehäusekörper erreicht wird. Es ist bei der erfindungsgemäßen Ausgestaltung auch als weiterer Vorteil anzuerkennen, daß das Gehäuse der hydrostatischen Maschine lediglich aus drei Bauteilen besteht, nämlich dem einstückigen Hauptgehäusekörper und den beiden Anbaugehäusekörpern.In the hydrostatic machine according to the invention, a first attachment housing body mounted on the main housing body is provided on which the pivot body of the first hydrostatic unit is mounted and a second attachment housing body adjoining the main housing body is provided on which the pivot body of the second hydrostatic unit is mounted. In this case, the first and the second mounting housing body form end-side mounting parts, which are arranged in the region of the front housing openings anyway required for the passage of the drive shafts, in the area while ensuring a simple design, a stable attachment of the mounting housing body to the main housing body is possible. In this case, the front-side openings can be formed so large that the cylinder drum and the swivel body of the first and second hydrostatic unit are each mounted by the frontal openings or can be disassembled. A significant advantage of the embodiment according to the invention can also be seen in that the pivot bearings are each realized on one and the same component, namely on the first and second mounting housing bodies. In this case, the respective bearing surfaces of the pivot bearing can be precisely manufactured on the attachment housing bodies not only in a simple manner and easily accessible but also in a clamping on a processing machine, whereby the quality of storage improves and the life of the pivot bearing is extended. Another advantage of the embodiment of the invention is that at the first and second Attachment housing body is formed both the pivot bearing and the bearing for the associated drive shaft, whereby not only a compact design but also a simple and accurate production of both bearing configurations is achieved in each case one and the same attachment housing body. It is also to be recognized as a further advantage in the embodiment according to the invention that the housing of the hydrostatic machine consists only of three components, namely the one-piece main housing body and the two attachment housing bodies.

Die Anbaugehäusekörper lassen sich als Bauteile ausbilden, die nach Lösung zugehöriger Befestigungselemente, insbesondere Befestigungsschrauben, um die Drehachse der zugehörigen Triebwelle drehbar sind und in unterschiedlichen Drehpositionen an den Hauptgehäusekörper anbaubar sind. Dies ist insbesondere dann von Vorteil, wenn die hydrostatischen Einheiten durch Axialkolbenmaschinen gebildet sind. Durch ein Anbauen der Anbaugehäusekörper in um 180° verdrehten Anbaustellungen lassen sich nämlich die Drehrichtung der miteinander verbundenen Triebwellen bestimmen. Hierdurch werden die Einsatzfähigkeit der hydrostatischen Maschine und deren Anpassung an verschiedene Betriebsbedingungen verbessert. Hierzu trägt auch bei, daß bei der erfindungsgemäßen Ausgestaltung die Triebwellen jeweils mit dem zugehörigen Anbaugehäusekörper eine Montageeinheit bilden können, wenn beide Montageeinheiten bezüglich einer sich rechtwinklig zu den Triebwellenachsen erstreckenden Mittelebene des Hauptgehäusekörpers spiegelsymmetrisch ausgebildet sind. Eine solche Ausgestaltung ermöglicht es, die hydrostatischen Einheiten bezüglich einer in der Mittelebene verlaufenden Querachse um 180° verdreht zu montieren. Hierdurch wird nicht nur erreicht, daß das Abtriebsende der Triebwellenanordnung wahlweise an der einen oder an der anderen Seite angeordnet werden kann, sondern es ist auch möglich, im vorbeschriebenen Sinne die Drehrichtung der hydraulischen Einheit zu bestimmten.The mounting housing body can be formed as components that are rotatable after solving associated fasteners, in particular fastening screws, about the axis of rotation of the associated drive shaft and are mountable in different rotational positions of the main housing body. This is particularly advantageous if the hydrostatic units are formed by axial piston machines. By attaching the attachment housing body in angled by 180 ° mounting positions can namely determine the direction of rotation of the interconnected drive shafts. This improves the operational capability of the hydrostatic machine and its adaptation to different operating conditions. This also contributes to the fact that in the embodiment according to the invention the drive shafts can each form a mounting unit with the associated mounting housing body, if both mounting units are mirror-symmetrical with respect to a perpendicular to the drive shaft axes extending center plane of the main housing body. Such a configuration makes it possible to mount the hydrostatic units rotated by 180 ° with respect to a transverse axis extending in the median plane. This not only ensures that the output end of the drive shaft assembly can be arranged either on one side or on the other, but it is also possible in the above sense, the direction of rotation of the hydraulic unit to certain.

Weitere Weiterbildungsmerkmale führen zu einfachen, kleinen bzw. kompakten und kostengünstig herstellbaren bzw. montierbaren Bauweisen, wodurch die hydrostatische Maschine im weiteren verbessert wird.Further development features lead to simple, small or compact and inexpensive to produce or assemble constructions, whereby the hydrostatic machine is further improved.

Nachfolgend werden die Erfindung und weitere durch sie erzielbare Vorteile anhand von vorteilhaften Ausgestaltungsmerkmalen eines Ausführungsbeispiels näher erläutert. Es zeigt:

Fig. 1
eine erfindungsgemäße hydrostatische Maschine im axialen Schnitt;
Fig. 2
die Maschine in einer um ihre Drehachse um 90° verdrehten Position, teilweise geschnitten;
Fig. 3
die Maschine in einer Position gemäß Fig. 1 in abgewandelter Ausgestaltung;
Fig. 4
die Maschine nach Fig. 3 in einer Position nach Fig. 1 in weiter abgewandelter Ausgestaltung;
Fig. 5
die Maschine nach Fig. 4 in weiter abgewandelter Ausgestaltung;
Fig. 6
die Maschine nach Fig. 5 in weiter abgewandelter Ausgestaltung;
Fig. 7
die Maschine nach Fig. 3 in weiter abgewandelter Ausgestaltung; und
Fig. 8
die Maschine nach Fig. 3 in weiter abgewandelter Ausgestaltung.
The invention and further achievable by them advantages are explained in more detail based on advantageous design features of an embodiment. It shows:
Fig. 1
a hydrostatic machine according to the invention in axial section;
Fig. 2
the machine in a rotated by 90 ° about its axis of rotation, partially cut;
Fig. 3
the machine in a position shown in Figure 1 in a modified embodiment.
Fig. 4
the machine of Figure 3 in a position according to Figure 1 in a further modified embodiment.
Fig. 5
the machine of Figure 4 in a further modified embodiment.
Fig. 6
the machine of Figure 5 in a further modified embodiment.
Fig. 7
the machine of Figure 3 in a further modified embodiment. and
Fig. 8
the machine of Fig. 3 in a further modified embodiment.

Die Hauptteile der in ihrer Gesamtheit mit 1 bezeichneten hydrostatischen Maschine sind ein Hauptgehäusekörper 2, zwei an diesen an einander gegenüberliegenden Stirnseiten angebauten Anbaugehäusekörper 3a, 3b, zwei Gehäusekammern 4a, 4b, in denen jeweils eine hydrostatische Einheit E1, E2, vorzugsweise in Form einer Kolbenmaschine 5a, 5b, angeordnet ist, wobei die Kolbenmaschinen 5a, 5b jeweils durch eine Verstellvorrichtung 6a, 6b bezüglich ihres Durchsatzvolumens verstellbar sind. Die Kolbenmaschinen 5a, 5b weisen jeweils eine Triebwelle 7a, 7b auf, die koaxial angeordnet sind, wobei die einander zugewandten Triebwellenenden mittels Lagern 8a, 8b an einer Gehäusemittelwand 9 drehbar gelagert sind, die sich zwischen den Gehäusekammern 4a, 4b erstreckt. Die einander abgewandten Enden der Triebwelle 7a, 7b sind mittels Drehlagern 11a, 11b an den Anbaugehäusekörpern 3a, 3b gelagert, die Durchgangslöcher aufweisen, in denen die Drehlager 11a, 11b angeordnet sind. In der Gehäusemittelwand 9 ist ein die Kammern 4a, 4b verbindender Kanal 9a vorgesehen, vorzugsweise im Bereich der Seite, an der die Verstellvorrichtungen 6a, 6b angeordnet sind.The main parts of the hydrostatic machine designated in its entirety by 1 are a main housing body 2, two attached to these at opposite end faces mounting housing body 3a, 3b, two housing chambers 4a, 4b, in each of which a hydrostatic unit E1, E2, preferably in the form of a piston machine 5a, 5b, is arranged, wherein the piston machines 5a, 5b are each adjustable by an adjusting device 6a, 6b with respect to their throughput volume. The piston machines 5a, 5b each have a drive shaft 7a, 7b, which are arranged coaxially, wherein the mutually facing drive shaft ends are rotatably supported by bearings 8a, 8b on a housing middle wall 9, which extends between the housing chambers 4a, 4b. The opposite ends of the drive shaft 7a, 7b are mounted by means of pivot bearings 11a, 11b on the mounting housing bodies 3a, 3b, which have through holes in which the pivot bearings 11a, 11b are arranged. A channel 9a connecting the chambers 4a, 4b is provided in the housing middle wall 9, preferably in the region of the side on which the adjusting devices 6a, 6b are arranged.

Die Kolbenmaschinen 5a, 5b weisen jeweils eine Zylindertrommel 13a, 13b auf, in der in etwa achsparallen und auf dem Umfang verteilt angeordneten Kolbenlöchern Kolben 14a, 14b hin und her verschiebbar gelagert sind, die durch an ihren nach außen weisenden Enden angeordnete sphärische Gelenke 15 mit in Gleitschuhen 16 schwenkbar gelagerten sphärischen Kolbenköpfen an einer Schrägscheibe 17a, 17b axial abgestützt sind, die an einem Schwenkkörper 17c mit zu beiden Seiten der Triebwelle 7a, 7b angeordneten Schwenkkufen eines Schwenklagers 18a, 18b mit kreisbogenförmigen konvexen Lagerflächen 19a an entsprechend kreisbogenförmigen konkaven Lagerflächen 19b an den Innenseiten der Anbaugehäusekörper 3a, 3b um Schwenkachsen 22a, 22b schwenkbar sind, die sich jeweils rechtwinklig zu den Drehachsen 21 der Triebwellen 7a, 7b erstrecken. Die hierzu vorgesehenen Schwenk- bzw. Verstellvorrichtungen 6a, 6b sind jeweils durch einen hydraulischen Kolbenzylinder gebildet, der durch ein Verbindungsgelenk 23 mit einem vom Schwenkkörper 17c nach innen ragenden Schwenkarm 24a, 24b verbunden sind. Die Kolbenzylinder erstrecken sich quer zur Drehachse 21, wobei sie sich in seitlichen Kammererweiterungen der Gehäusekammer 4a, 4b befinden und im Hauptgehäusekörper 2 entsprechend verschiebbar gelagert sind.The piston machines 5a, 5b each have a cylinder drum 13a, 13b, in which approximately axially parallel and circumferentially distributed piston holes piston 14a, 14b are mounted reciprocally displaceable, which arranged by at their outwardly facing ends spherical joints 15 with in sliding shoes 16 pivotally mounted spherical piston heads on a swash plate 17a, 17b are axially supported on a pivot body 17c with arranged on both sides of the drive shaft 7a, 7b pivot skids of a pivot bearing 18a, 18b with circular arc-shaped convex bearing surfaces 19a on corresponding arcuate concave bearing surfaces 19b the inner sides of the mounting housing body 3a, 3b are pivotable about pivot axes 22a, 22b, each extending at right angles to the axes of rotation 21 of the drive shafts 7a, 7b. The pivoting or adjusting devices 6a, 6b provided for this purpose are each formed by a hydraulic piston cylinder, which are connected by a connecting joint 23 to a swivel arm 24a, 24b protruding inwardly from the swivel body 17c. The piston cylinders extend transversely to the axis of rotation 21, wherein they are located in lateral chamber extensions of the housing chamber 4a, 4b and are mounted correspondingly displaceable in the main housing body 2.

Die Schrägscheiben 17a, 17b umgeben die zugehörige Triebwelle 7a, 7b ringförmig. Die Zylindertrommeln 13a, 13b sind jeweils drehfest mit der zugehörigen Triebwelle 7a, 7b verbunden, und sie liegen mit ihren nach innen gerichteten Stirnseiten jeweils an einer Steuerscheibe 25a, 25b mit Steueröffnungen an, die durch in der Gehäusemittelwand 9 verlaufende Zuführungskanälen 26a, 26b und Abführungskanäle 27a, 27b mit in Fig. 1 nicht dargestellten, am Hauptgehäusekörper 2 angeordneten Einlässen und Auslässen für ein hydraulisches Medium, insbesondere Hydrauliköl, verbunden sind.The swash plates 17a, 17b surround the associated drive shaft 7a, 7b annularly. The cylinder drums 13a, 13b are respectively non-rotatably connected to the associated drive shaft 7a, 7b, and they rest with their inwardly facing end faces in each case on a control disk 25a, 25b with control openings which extend through in the housing middle wall 9 supply channels 26a, 26b and discharge channels 27a, 27b are not shown in Fig. 1, arranged on the main housing body 2 inlets and outlets for a hydraulic medium, in particular hydraulic oil, are connected.

Die einander zugewandten Enden der Triebwellen 7a, 7b sind vorzugsweise drehfest miteinander verbunden. Hierzu kann eine Kupplung 28, z. B. in Form einer Kupplungshülse 28a, dienen, die die beiden Triebwellenenden muffenförmig übergreift und z. B. durch an der Mantelfläche der Triebwellenenden und an der Innenmantelfläche der Kupplungshülse 28a angeordnete, ineinandergreifende Zähnen formschlüssig miteinander verbunden sind. Die Kupplungshülse 28a weist einen radialen Abstand von der Innenwandung des vorhandenen Lagerlochs in der Gehäusemittelwand 9 auf. Die Außenzähne an den Triebwellenenden und vorzugsweise auch die Innenzähne an der Kupplungshülse 28a bzw. deren Zahnflanken sind vorzugsweise um die Triebwellenenden quer durchsetzende Achsen konvex gekrümmt. Durch eine solche "ballige" Verzahnung können geringfügige Kippstellungen der Triebwellen 7a, 7b ausgeglichen werden, die aufgrund vorhandener Herstellungstoleranzen kaum zu vermeiden sind. Die Triebwellen 7a, 7b können somit von einer idealen koaxialen Anordnung geringfügig abweichen, wodurch Durchbiegungen der Triebwellen 7a, 7b vermieden werden.The mutually facing ends of the drive shafts 7a, 7b are preferably connected to each other in a rotationally fixed manner. For this purpose, a coupling 28, z. B. in the form of a coupling sleeve 28 a serve, which engages over the two drive shaft ends sleeve-shaped and z. B. by arranged on the lateral surface of the drive shaft ends and on the inner circumferential surface of the coupling sleeve 28a, interlocking teeth are positively connected with each other. The coupling sleeve 28a has a radial distance from the inner wall of the existing bearing hole in the housing middle wall 9. The outer teeth on the drive shaft ends and preferably also the inner teeth on the coupling sleeve 28a or their tooth flanks are preferably curved convexly around the drive shaft ends transversely traversing axes. By such a "crowned" toothing slight tilting positions of the drive shafts 7a, 7b can be compensated, which are difficult to avoid due to existing manufacturing tolerances. The drive shafts 7a, 7b can thus deviate slightly from an ideal coaxial arrangement, as a result of which deflections of the drive shafts 7a, 7b are avoided.

Die Ausgestaltungen und Funktionen der Kolbenmaschinen 5a, 5b sind im einzelnen bekannt und brauchen deshalb nicht weiter beschrieben zu werden.The embodiments and functions of the reciprocating engines 5a, 5b are known in detail and therefore need not be further described.

Die Anbaugehäusekörper 3a, 3b weisen jeweils eine radiale Körperwand 3c auf, an deren Innenseiten die Lagerflächen 19 für den Schwenkkörper 17c ausgebildet sind. Im Rahmen der Erfindung können die Körperwände 3c direkt an stirnseitigen Anbauflächen 29 am Hauptgehäusekörper 2 angebaut und abgedichtet sein. Beim vorliegenden Ausführungsbeispiel sind die Anbaugehäusekörper 3a, 3b mit von den Körperwänden 3c jeweils nach innen ragenden Umfangswänden 3e topfförmig ausgebildet, wobei die Umfangswände 3d mit ihren stirnseitigen Anbauflächen 31 an den Anbauflächen 29 anliegen und abgedichtet sind. Zum Zweck der Zentrierung und der radial formschlüssigen Befestigung ist es vorteilhaft, die Anbauflächen 29, 31 stufenförmig auszubilden, wodurch die Anbauflächen mit ineinander greifenden zapfen- und hohlzapfenförmigen Zentrierflächen 32 kombiniert sind. Zur Abdichtung ist vorzugsweise ein Dichtring 33, z. B. O-Ring, vorgesehen, der den Zentrierflächen 32 in einer Außenringnut oder Innenringnut in an sich bekannter Weise zugeordnet ist.The attachment housing body 3a, 3b each have a radial body wall 3c, on the inner sides of the bearing surfaces 19 are formed for the pivot body 17c. In the context of the invention, the body walls 3c can be mounted and sealed directly on frontal mounting surfaces 29 on the main housing body 2. In the present embodiment, the mounting housing body 3a, 3b formed with the body walls 3c in each case inwardly projecting peripheral walls 3e pot-shaped, wherein the peripheral walls 3d abut with their frontal Anbauflächen 31 on the cultivation surfaces 29 and sealed. For the purpose of centering and the radial positive fastening, it is advantageous to form the cultivation surfaces 29, 31 step-shaped, whereby the cultivation surfaces are combined with interengaging spigot and hollow pin-shaped centering surfaces 32. For sealing is preferably a sealing ring 33, for. B. O-ring, provided, which is associated with the centering surfaces 32 in an outer ring groove or inner ring groove in a conventional manner.

Es ist vorteilhaft, die hydrostatische Maschine 1 bezüglich einer sich zwischen den Kolbenmaschinen 5a, 5b im Bereich der Gehäusemittelwand 9 rechtwinklig zur gemeinsamen Drehachse 21 erstreckenden Mittelebene E so spiegelbildlich auszubilden, daß die Kolbenmaschinen 5a, 5b vorzugsweise mit den zugehörigen Anbaugehäusekörpern 3a, 3b in um 180° verdrehten Stellungen am Hauptgehäusekörper 2 montierbar sind. Dies ist insbesondere dann vorteilhaft, wenn die Anbaugehäusekörper 3a, 3b an ihren dem Hauptgehäusekörper 2 zugewandten Seiten gleich, jedoch an ihren einander abgewandten Seiten unterschiedlich ausgebildet sind. In diesem Falle können durch die unterschiedliche Ausbildung der Anbaugehäusekörper 3a, 3b vorgegebene unterschiedliche Anbausituationen wahlweise an der einen oder an der anderen Seite des Hauptgehäusekörpers 2 geschaffen werden. Beim vorliegenden Ausführungsbeispiel dient der vom Triebwellenzapfen 7c der Triebwelle 7a durchsetzte, hier linke, Anbaugehäusekörper 3a mit einer ringstufenförmigen Anbaufläche 34 dem Anbau der hydrostatischen Maschine 1 an einen nicht dargestellten Träger. Der andere Anbaugehäusekörper 3b kann dem Anbau von wenigstens einem weiteren Aggregat oder einer weiteren hydraulischen Einheit E3 dienen, z. B. einer Hilfspumpe, die in Fig. 1 nicht dargestellt ist.It is advantageous to form the hydrostatic machine 1 with respect to a between the piston machines 5a, 5b in the region of the housing center wall 9 perpendicular to the common axis of rotation 21 extending center plane E mirror image that the reciprocating engines 5a, 5b preferably with the associated mounting housing bodies 3a, 3b in order 180 ° rotated positions on the main housing body 2 can be mounted. This is particularly advantageous when the attachment housing body 3a, 3b at their sides facing the main housing body 2 equal, but are formed differently on their sides facing away from each other. In this case, given by the different design of the mounting housing body 3a, 3b predetermined different mounting situations can be created either on one side or on the other side of the main housing body 2. At the The present embodiment is used by the drive shaft journal 7c of the drive shaft 7a interspersed, here left, mounting housing body 3a with an annular stepped mounting surface 34 the cultivation of the hydrostatic machine 1 to a support, not shown. The other attachment housing body 3b can serve for the cultivation of at least one further unit or a further hydraulic unit E3, z. B. an auxiliary pump, which is not shown in Fig. 1.

Es ist auch vorteilhaft, die zwischen den Anbaugehäusekörpern 3a, 3b und dem Hauptgehäusekörper 2 wirksamen Befestigungsmittel so auszubilden, daß die Anbaugehäusekörper 3a, 3b wahlweise in um die Drehachse 21 180° verdrehten Positionen an den Hauptgehäusekörper 2 anbaubar und mit der zugehörigen Verstellvorrichtung Ga, Gb verbindbar sind. Hierdurch läßt sich jeweils die Drehrichtung der Kolbenmaschinen 5a, 5b umkehren und an am Einbauort vorhandene Erfordernisse anpassen.It is also advantageous to design the fastening means effective between the attachment housing bodies 3a, 3b and the main housing body 2 in such a way that the attachment housing bodies 3a, 3b can be optionally mounted on the main housing body 2 in positions rotated 180 ° about the rotation axis 180 and with the associated adjustment device Ga, Gb are connectable. As a result, in each case the direction of rotation of the reciprocating machines 5 a, 5 b can be reversed and adapted to existing requirements at the installation site.

Beim Ausführungsbeispiel nach Fig. 2 ist der dem Triebzapfen 7c abgewandte Anbaugehäusekörper 3b Träger einer dritten hydraulischen Einheit E3 oder eines Zusatzaggregates, hier in Form einer Hilfspumpe 35, die von einem verlängerten Antriebszapfen 7d der zugehörigen Triebwelle 7b angetrieben wird. Es handelt sich z. B. um eine Zahnradpumpe, mit wenigstens einem Förderzahnrad 35, das direkt auf dem Antriebszapfen 7d befestigt ist oder auf einer Hülse 36 drehfest sitzt, die drehfest mit dem Antriebszapfen 7d verbunden ist. Bei dieser Ausgestaltung ist die radiale Körperwand 3c verbreitert, wobei in ihr vorzugsweise am Umfang ein Einlaß 37 und ein Auslaß 38 angeordnet sind, von denen sich jeweils Verbindungskanäle 39, 41 zur Druck- und Niederdruckzone der Zahnradpumpe erstrecken. Das Förderzahnrad 35 befindet sich in einer Kammer einer Anbauplatte 42, die stirnseitig an die Körperwand 3c angebaut ist und dabei vorzugsweise in eine Ausnehmung in der Körperwand 3c einfaßt und darin zentriert ist. Das Gehäuse 2b der dritten hydrostatischen Einheit E3 ist mit 2b bezeichnet.In the embodiment according to FIG. 2, the attachment housing body 3b facing away from the drive pin 7c carries a third hydraulic unit E3 or an additional unit, here in the form of an auxiliary pump 35, which is driven by an extended drive pin 7d of the associated drive shaft 7b. It is z. Example, to a gear pump, with at least one feed gear 35 which is mounted directly on the drive pin 7 d or rotatably seated on a sleeve 36 which is rotatably connected to the drive pin 7 d. In this embodiment, the radial body wall 3c is widened, wherein in it preferably at the periphery of an inlet 37 and an outlet 38 are arranged, of which each connecting channels 39, 41 extend to the pressure and low pressure zone of the gear pump. The conveyor gear 35 is located in a chamber of a mounting plate 42 which is mounted on the front side of the body wall 3c and thereby preferably in a recess in the body wall 3c and centered therein is. The housing 2b of the third hydrostatic unit E3 is designated by 2b.

Beim Ausführungsbeispiel nach Fig. 3, bei dem gleiche oder vergleichbare Teile ebenfalls mit gleichen Bezugszeichen versehen sind, ist der dem Triebzapfen 7c gegenüberliegend angeordnete Anbaugehäusekörper 3b ebenfalls ein vorzugsweise einstückiges Teil einer dritten hydraulischen Einheit E3, die vorzugsweise durch eine Kolbenmaschine 5c, insbesondere eine Axialkolbenmaschine, gebildet ist. Die Kolbenmaschine 5c kann bezüglich ihres Durchsatzvolumens konstant oder verstellbar sein. Es kann sich um eine Schrägscheibenmaschine handeln, deren Zylindertrommel 13c drehfest auf einer insbesondere einstückigen Triebwellenverlängerung 45 gelagert ist. Die Triebwellenverlängerung 45 kann in an sich bekannter Weise die Zylindertrommel 13c sowie eine an deren äußeren Stirnseite angeordnete Steuerscheibe 46 axial in Aufnahmelöchern durchsetzen und mit einem Lagerzapfen 45a mittels eines Drehlagers 47 an einem Deckel 48 gelagert sein, der gegebenenfalls Teil einer vierten hydraulischen Einheit E4 sein kann, bei der es sich um eine Hilfspumpe mit einem Gehäuse 2c handeln kann.In the embodiment of Fig. 3, in which the same or similar parts are also provided with the same reference numerals, the drive pin 7c oppositely disposed mounting housing body 3b is also preferably a one-piece part of a third hydraulic unit E3, preferably by a piston machine 5c, in particular an axial piston machine , is formed. The piston engine 5c may be constant or adjustable with regard to its throughput volume. It can be a swashplate machine whose cylindrical drum 13c is mounted non-rotatably on a drive shaft extension 45 which is in particular one-piece. The drive shaft extension 45 can in a conventional manner, the cylinder drum 13c and arranged on the outer end face cam 46 axially pass through in receiving holes and be stored with a bearing pin 45a by means of a pivot bearing 47 on a lid 48, which may be part of a fourth hydraulic unit E4 can, which may be an auxiliary pump with a housing 2c.

Der Deckel 48 bzw. der Körper der Hilfspumpe ist an einer sich einstückig von der Körperwand 3c erstreckenden Umfangswand 49 dicht angebaut, z. B. verschraubt, die eine dritte Arbeitskammer 51 umgibt, in der die dritte hydraulische Einheit E3 in an sich bekannter Weise angeordnet ist. Die Schrägscheibe 17c der Schrägscheibenmaschine 5c ist an der radialen Körperwand 3c gelagert. Bei der Triebwellenverlängerung 45 kann es sich um eine separate Triebwelle handeln, deren inneres Triebwellenende durch ein Drehlager 53 in einem Lagerloch der radialen Körperwand 3c drehbar gelagert ist. In beiden Fällen - Triebwellenverlängerung 45 oder separate Triebwelle - können im Bereich der radialen Körperwand 3c zwei Drehlager 11b, 53 axial nebeneinander angeordnet sein, wie es Fig. 3 zeigt.The lid 48 and the body of the auxiliary pump is tightly attached to an integrally extending from the body wall 3 c peripheral wall 49, z. B. screwed surrounding a third working chamber 51, in which the third hydraulic unit E3 is arranged in a conventional manner. The swash plate 17c of the swash plate machine 5c is supported on the radial body wall 3c. In the drive shaft extension 45 may be a separate drive shaft, the inner drive shaft end is rotatably supported by a pivot bearing 53 in a bearing hole of the radial body wall 3c. In both cases - drive shaft extension 45 or separate drive shaft - in the region of the radial body wall 3c, two pivot bearings 11b, 53 can be arranged axially next to one another, as shown in FIG.

Die hydraulischen Versorgungsleitungen und -kanäle für die Kolbenmaschine 5c sind von an sich bekannter Art und aus Vereinfachungsgründen nicht näher beschrieben. Wenn es sich bei der Triebwelle 54 für die dritte Kolbenmaschine 43 um eine separate Triebwelle handelt, kann deren Triebwellenende formschlüssig mit dem gegenüberliegenden Triebwellenende der Triebwelle 7b verbunden sein, z. B. formschlüssig durch eine Kupplung 28, wie es beim Ausführungsbeispiel nach Fig. 1 bereits beschrieben worden ist. Bei der Hilfspumpe kann es sich z. B. um eine Zahnradpumpe handeln, die beim Ausführungsbeispiel nach Fig. 1 beschrieben ist.The hydraulic supply lines and channels for the piston engine 5c are of a known type and for reasons of simplicity not described in detail. If the drive shaft 54 for the third piston engine 43 is a separate drive shaft, its drive shaft end can be positively connected to the opposite drive shaft end of the drive shaft 7b, z. B. positively by a clutch 28, as has already been described in the embodiment of FIG. 1. When the auxiliary pump can be such. B. is a gear pump, which is described in the embodiment of FIG. 1.

Beim Ausführungsbeispiel nach Fig. 4, das weitgehend dem Ausführungsbeispiel nach Fig. 3 entsprechen kann, ist der axial äußere Lagerzapfen 54 der zusätzlichen Triebwelle oder der Triebwellenverlängerung 45 stirnseitig durch einen Kupplungszapfen 55 koaxial verlängert, der formschlüssig in eine Kupplungshülse 56 einfaßt, z. B. im Sinne einer Zahn- oder Vielzahnkupplung, wobei die Kupplungshülse 56 treibendes Teil der Hilfspumpe sein kann.In the embodiment of FIG. 4, which may largely correspond to the embodiment of FIG. 3, the axially outer bearing pin 54 of the additional drive shaft or the drive shaft extension 45 end face by a coupling pin 55 coaxially extended, which engages positively in a coupling sleeve 56, z. B. in the sense of a toothed or multi-tooth clutch, wherein the coupling sleeve 56 may be driving part of the auxiliary pump.

Beim Ausführungsbeispiel nach Fig. 5 bei dem gleiche oder vergleichbare Teile ebenfalls mit gleichen Bezugszeichen versehen sind, ist das Schwenklager 18 der zweiten hydrostatischen Einheit E2 ebenfalls am Anbaugehäuseköper 3b angeordnet, der Teil des Gehäuses 2b der dritten hydrostatischen Einheit E3 ist, die vorzugsweise ebenfalls durch eine Kolbenmaschine 5c, insbesondere eine Axialkolbenmaschine, gebildet ist. Die Kolbenmaschine 5c ist bezüglich ihres Durchsatzvolumens vorzugsweise verstellbar, wobei es sich um eine Schrägscheibenmaschine handeln kann, deren Schrägscheibe 17c schwenkbar gelagert ist. Die Schwenkebene des zugehörigen Schwenklagers 18c ist bezüglich des benachbarten bzw. zweiten Schwenklagers 18b bzw. auch bezüglich des ersten Schwenklagers 18a um 90° verdreht angeordnet, wie es Fig. 5 zeigt. Das Schwenklager 18c kann jedoch auch die gleiche Schwenkebene aufweisen.In the embodiment of FIG. 5 are also provided with the same or comparable parts with the same reference numerals, the pivot bearing 18 of the second hydrostatic unit E2 is also arranged on Anbaugehäuseköper 3b, which is part of the housing 2b of the third hydrostatic unit E3, preferably also by a piston machine 5c, in particular an axial piston machine, is formed. The piston engine 5c is preferably adjustable in terms of its throughput volume, which may be a swash plate machine, the swash plate 17c is pivotally mounted. The pivoting plane of the associated pivot bearing 18c is arranged rotated by 90 ° with respect to the adjacent or second pivot bearing 18b and also with respect to the first pivot bearing 18a, as shown in FIG. 5. However, the pivot bearing 18 c may also have the same pivoting plane.

Bei der Kolbenmaschine 5c kann die zugehörige Verstellvorrichtung 6c eine solche automotive Verstellvorrichtung 6c sein, die mit steigendem Arbeitsdruck das Durchsatzvolumen verringert und mit fallendem Arbeitsdruck das Durchsatzvolumen vergrößert. Hierzu kann die Schrägscheibe 17c durch eine Feder in ihre maximale Schwenkstellung verstellt werden, wobei mit steigendem Arbeitsdruck die Schrägscheibe 17c gegen die Kraft der Feder in Richtung ihrer minimalen Volumeneinstellung verstellt wird. Beim vorliegenden Ausführungsbeispiel ist die Feder 58 durch eine Druckfeder gebildet, die auf der Druckseite der Schrägscheibe 17c zwischen dieser und der Körperwand 3c angeordnet ist. Die Umfangswand 49 des Gehäuses 2b ist bei diesem Ausführungsbeispiel durch einen an ihrem Rand anliegenden Deckel 48 verschlossen, an dem das Drehlager 47 für die zugehörige Triebwelle abgestützt ist. Bei dieser Triebwelle kann es sich um eine Triebwellenverlängerung oder um eine separate Triebwelle handeln, wie es bereits beschrieben worden ist. Fig. 6 zeigt das Ausführungsbeispiel nach Fig. 5 in einer um 90° gedrehten Teilschnitt-Darstellung.In the piston machine 5c, the associated adjusting device 6c may be such a automotive adjusting device 6c, which reduces the throughput volume with increasing working pressure and increases the throughput volume with decreasing working pressure. For this purpose, the swash plate 17c can be adjusted by a spring in its maximum pivot position, with the increasing working pressure, the swash plate 17c is adjusted against the force of the spring in the direction of their minimum volume setting. In the present embodiment, the spring 58 is formed by a compression spring disposed on the pressure side of the swash plate 17c between it and the body wall 3c. The peripheral wall 49 of the housing 2b is closed in this embodiment by a voltage applied to its edge cover 48, on which the pivot bearing 47 is supported for the associated drive shaft. This drive shaft may be a drive shaft extension or a separate drive shaft, as has already been described. Fig. 6 shows the embodiment of FIG. 5 in a rotated by 90 ° partial section view.

Das Ausführungsbeispiel nach Fig. 7, bei dem gleiche oder vergleichbare Teile mit gleichen Bezugszeichen versehen sind, basiert auf dem Ausführungsbeispiel nach Fig. 3, wobei jedoch ein gemeinsames Drehlager 61 für das äußere Triebwellenende der Triebwelle 7b und das innere Triebwellenende einer separaten Triebwelle 7c der dritten hydrostatischen Einheit E3 vorgesehen ist. Das gemeinsame Drehlager 61 ist dadurch gebildet, daß das äußere Ende der Triebwelle 7b und das innere Ende der Triebwelle 7c koaxial muffenförmig ineinander greifen, wobei das übergreifende Teil in einem Lager der Körperwand 3c drehbar gelagert ist. Beim vorliegenden Ausführungsbeispiel ist ein gemeinsames Wälzlager 52 vorgesehen, das auf dem übergreifenden Teil sitzt. Dies ist vorzugsweise dadurch gebildet, daß das äußere Ende der Triebwelle 7b mit einer koaxialen, insbesondere hohlzylindrischen Ausnehmung 63 als Lagerhülse 64 ausgebildet ist, in der das entsprechend geformte innere Ende der Triebwelle 7c sitzt und drehfest verbunden ist, z. B. durch eine Ein- oder Mehrteil-Verbindung oder ein Einschraubgewinde.The embodiment of FIG. 7, wherein the same or similar parts are provided with the same reference numerals, based on the embodiment of FIG. 3, but with a common pivot bearing 61 for the outer drive shaft end of the drive shaft 7b and the inner drive shaft end of a separate drive shaft 7c of third hydrostatic unit E3 is provided. The common pivot bearing 61 is formed by the fact that the outer end of the drive shaft 7b and the inner end of the drive shaft 7c cooperate coaxially sleeve-shaped, wherein the cross-part is rotatably mounted in a bearing of the body wall 3c. In the present embodiment, a common roller bearing 52 is provided, which sits on the overarching part. This is preferably formed by the fact that the outer end of the drive shaft 7b with a coaxial, in particular hollow cylindrical recess 63 as a bearing sleeve 64 is formed, in which the correspondingly shaped inner end of the drive shaft 7c is seated and rotatably connected, for. B. by a single or multi-part connection or a screw thread.

Das Ausführungsbeispiel nach Fig. 8, bei dem ebenfalls gleich oder vergleichbare Teile mit gleichen Bezugszeichen versehen sind, unterscheidet sich von dem Ausführungsbeispiel nach Fig. 7 dadurch, daß das gemeinsame Drehlager 61 durch eine separate Lagerhülse 64a gebildet ist, in die von beiden Stirnseiten her die Triebwellen 7b, 7c mit entsprechend angepaßten Lagerzapfen fest eingesetzt sind, z. B. durch eine Keil- oder Schraubverbindung. Die Lagerzapfen können mit ihren freien Stirnenden direkt aneinander anliegen oder die Triebwellen 7b, 7c können mit Schulterflächen an den Stirnenden der Lagerhülse 64 anliegen und somit axial begrenzt und positioniert sein. Zur Sicherung des Wälzlagers 62 auf der Lagerhülse 64a sind ebenfalls zwei das Wälzlager 62 axial begrenzende Schulterflächen der Lagerhülse 64a vorgesehen. Beim vorliegenden Ausführungsbeispiel ist die eine Schulterfläche durch einen vorzugsweise einstückig angeformten Ringansatz auf der Lagerhülse 64 gebildet, während die andere Schulterfläche durch einen lösbaren Sicherungsring gebildet ist, der in einer Ringnut sitzt. Das Wälzlager 62 ist von der dem Hauptgehäusekörper 2 zugewandten Seite her montierbar bzw. demontierbar. Es liegt mit seiner dem Hauptgehäusekörper 2 abgewandten Seite an einer Schulterfläche 65 im Gehäuse 2b bzw. in der Körperwand 3c an.The embodiment of FIG. 8, in which also the same or comparable parts are provided with the same reference numerals, differs from the embodiment of FIG. 7 in that the common pivot bearing 61 is formed by a separate bearing sleeve 64 a, in the from both end sides the drive shafts 7b, 7c are firmly inserted with appropriately adapted bearing journals, z. B. by a wedge or screw. The trunnions can bear directly against each other with their free ends or the drive shafts 7b, 7c can rest with shoulder surfaces on the front ends of the bearing sleeve 64 and thus be axially limited and positioned. To secure the rolling bearing 62 on the bearing sleeve 64a, two rolling bearings 62 axially limiting shoulder surfaces of the bearing sleeve 64a are also provided. In the present embodiment, the one shoulder surface is formed by a preferably integrally formed annular shoulder on the bearing sleeve 64, while the other shoulder surface is formed by a releasable locking ring which sits in an annular groove. The roller bearing 62 can be mounted or dismounted from the side facing the main housing body 2. It lies with its side facing away from the main housing body 2 on a shoulder surface 65 in the housing 2b and in the body wall 3c.

Bei allen vorbeschriebenen Ausgestaltungen kann ein Anbaugehäusekörper, gemäß Fig. 1 der Anbaugehäusekörper 3a, als Anbauflansch für die so gebildete Mehrfachhydraulikeinheit dienen, wobei der andere Anbaugehäusekörper 3b die Funktion der Durchtriebsmöglichkeit übernimmt.In all the above-described embodiments, a mounting housing body, as shown in FIG. 1, the mounting housing body 3a, serve as mounting flange for the multiple hydraulic unit thus formed, the other attachment housing body 3b assumes the function of Durchtriebsmöglichkeit.

Aufgrund der an beiden Seiten des Hauptgehäusekörpers 2 gleichen Anschlußbedingungen für die Anbaugehäusekörper 3a, 3b können letztere vertauscht und Montage-Varianten erreicht werden, die bezüglich des Triebzapfens 7c der zugehörigen Triebwelle 7a wahlweise rechts oder links sein können.Due to the same on both sides of the main housing body 2 connection conditions for the attachment housing body 3a, 3b, the latter can be reversed and assembly variants can be achieved, which can be either right or left with respect to the drive pin 7c of the associated drive shaft 7a.

Es ist außerdem vorteilhaft, die Verstellvorrichtungen 6a, 6b in den Hauptgehäusekörper 2 zu integrieren zur direkten Versorgung der beiden Verstellvorrichtungen 6a, 6b. Hierdurch entfallen zusätzliche Anbauflächen am Hauptgehäusekörper 2, und außerdem wird eine kleine und kompakte sowie für die Verstellvorrichtungen 6a, 6b geschützte Bauweise erreicht. Ferner ist es vorteilhaft, nur eine interne Tankverbindung und eine Speisekreis-Druckabsicherung für die erste und die zweite hydraulische Einheit E1, E2 vorzusehen. Hierfür bedarf es nur eines einzigen Tankanschlusses. Dabei ist es vorteilhaft, die Einspeisung im Zentrum des Hauptgehäusekörpers 2 vor einem Einspeise-Druckbegrenzungsventil anzuordnen. Das über ein Druckbegrenzungsventil ausgeströmte hydraulische Medium wird über die Gehäusekammern 4a, 4b mittels einer internen Verbindung am Tankanschluß zum Tank zurückgeführt.It is also advantageous to integrate the adjusting devices 6a, 6b in the main housing body 2 for the direct supply of the two adjusting devices 6a, 6b. This eliminates additional acreage on the main housing body 2, and also a small and compact and for the adjusting devices 6a, 6b protected construction is achieved. Furthermore, it is advantageous to provide only an internal tank connection and a supply pressure protection for the first and the second hydraulic unit E1, E2. This requires only a single tank connection. It is advantageous to arrange the feed in the center of the main housing body 2 in front of a feed pressure relief valve. The discharged via a pressure relief valve hydraulic medium is returned via the housing chambers 4a, 4b by means of an internal connection at the tank connection to the tank.

Der den Triebwellenzapfen 7c umgebende bzw. in dessen Nähe befindliche vordere Anbaugehäusekörper 3a kann bei Gewährleistung einer stabilen Bauweise und Befestigung einen Flansch zum Anbau der kompletten Mehrfachhydraulikeinheit bilden. In diesem Falle trägt der andere bzw. hintere Anbaugehäusekörper 3b das Triebwellenlager und das Schwenkkörperlager der zweiten hydraulischen Einheit, und er kann auch Träger eines angegossenen Gehäuses mit Saug- und Druckanschlüssen für eine dritte hydraulische Einheit E3, z. B. eine ZahnradMaschine oder eine Kolbenmaschine, bilden. Dabei lassen sich auch verschieden Durchtriebsvarianten ausführen. Hierdurch läßt sich ein Durchtriebs-Adapter und das Anflanschschild der dritten hydraulischen Einheit einsparen. Außerdem führt diese Ausgestaltung zu einer wesentlichen Baulängen-Reduzierung.The drive shaft journal 7c surrounding or located in its vicinity front attachment housing body 3a can form a flange for mounting the complete multiple hydraulic unit while ensuring a stable construction and attachment. In this case, the other or rear cultivation housing body 3b carries the drive shaft bearing and the swivel body bearing of the second hydraulic unit, and it can also support a molded housing with suction and pressure connections for a third hydraulic unit E3, z. As a gear machine or a piston machine form. In this case, different drive-through variants can also be carried out. This allows a through drive adapter and the Anflanschschild the third hydraulic unit save on. In addition, this embodiment leads to a significant reduction in length.

Aufgrund der symmetrischen Ausbildung des Hauptgehäusekörpers 2 bezüglich seiner quer verlaufenden Mittelebene E und einer entsprechend symmetrischen Anordnung und Ausbildung der Anbaugehäusekörper 3a, 3b können letztere beliebig angebaut werden. Hierdurch werden Montage-Varianten erreicht. Durch Drehen der Anbaugehäusekörper 3a, 3b um 180° in einer deren Mittelachse 21 enthaltenen Längsebene können verschiedene bauliche Belange und Drehrichtungs-Varianten erfüllt werden.Due to the symmetrical design of the main housing body 2 with respect to its transverse center plane E and a correspondingly symmetrical arrangement and design of the mounting housing body 3a, 3b, the latter can be grown arbitrarily. As a result, assembly variants are achieved. By rotating the attachment housing body 3a, 3b by 180 ° in a longitudinal axis of its central axis 21 contained various structural issues and directions of rotation can be met.

Durch ein Zusammenfassen der Triebwellen-Lagerung der zweiten und der dritten hydraulischen Einheit E2, E3 (Fig. 7 und 8) erreicht man die Einsparung eines Drehlagers und auch eine Baulängenveringerung. Diese Ausgestaltungen können auch bei den übrigen Ausführungsbeispielen ausgeführt werden.By combining the drive shaft bearing of the second and the third hydraulic unit E2, E3 (FIGS. 7 and 8), the saving of a pivot bearing and also a length reduction are achieved. These embodiments can also be carried out in the other embodiments.

Es ist im übrigen vorteilhaft, eine Kupplung 28 zwischen den Triebwellen 7a, 7b oder auch 7c jeweils im Sinne eines räumlichen Gelenks allbeweglich, z. B. "ballig", auszuführen, um aus nicht vermeidbaren Toleranzen Durchbiegungen der Triebwellen zu vermeiden.It is also advantageous, a clutch 28 between the drive shafts 7a, 7b or 7c each in the sense of a spatial joint allbeweglich, z. B. "spherical", run to avoid unavoidable tolerances deflections of the drive shafts.

Claims (17)

  1. Hydrostatic machine (1) comprising
    at least one first hydrostatic unit (E1) and one second hydrostatic unit (E2), each hydrostatic unit (E1, E2) having respective pistons (14a, 14b) guided in respective cylinder drums (13a, 13b) and supported by respective swivelling bodies (17a, 17b) which can be adjusted by respective adjusting devices (6a, 6b), and having respective control bodies (25a, 25b),
    and a one-piece main housing body (2) which radially surrounds the cylinder drums (13a, 13b), the control bodies (25a, 25b) and the adjusting devices (6a, 6b) of both hydrostatic units (E1, E2) and has pressure channels for supplying a pressure medium to and discharging it from the control bodies (25a, 25b) of both hydrostatic units (E1, E2),
    characterised by
    a first add-on housing body (3a) which is arranged on a first side of the main housing body (2) and on which the swivelling body (17a) of the first hydrostatic unit (E1) is mounted,
    and a second add-on housing body (3b) which is arranged on a second side of the main housing body (2) and on which the swivelling body (17b) of the second hydrostatic unit (E2) is mounted.
  2. Hydrostatic machine according to Claim 1,
    characterised in that the swivelling bodies (17a, 17b) are each swivellably mounted, by circular-segment-shaped convex bearing surfaces (19a), on concave circular-segment-shaped bearing surfaces (19b) arranged internally on the add-on housing bodies (3a, 3b).
  3. Hydrostatic machine according to Claim 1 or 2,
    characterised in that the add-on housing bodies (3a, 3b) are each formed by an approximately radially extending body wall (3c) and a peripheral wall (3d) extending from the latter in the direction of the main housing body (2).
  4. Hydrostatic machine according to one of the preceding claims, characterised in that the cylinder drums (13a, 13b) are mounted on drive shafts (7a, 7b), the outer drive-shaft ends of which are each supported on the associated add-on housing body (3a, 3b) by a rotary bearing (11a, 11b).
  5. Hydrostatic machine according to one of the preceding claims, characterised in that the adjusting devices (6a, 6b) are integrated into the main housing body (2), in particular in chamber extensions of housing chambers (4a, 4b) of the main housing body (2) which receive the cylinder drums (13a, 13b).
  6. Hydrostatic machine according to one of the preceding claims, characterised in that the hydrostatic units (E1, E2) are formed by axial piston machines (5a, 5b).
  7. Hydrostatic machine according to Claim 6, characterised in that one add-on housing body or both add-on housing bodies (3a, 3b) is or are mountable in positions on the main housing body (2) which are arranged such that they are rotated through 180° relative to each other about the axis of rotation (21) of the associated cylinder drum (13a, 13b).
  8. Hydrostatic machine according to one of the preceding claims, characterised in that the first side and the second side of the main housing body (2) are mutually opposite sides.
  9. Hydrostatic machine according to one of the preceding claims, characterised in that the bearing surfaces, bearing against each other, between the main housing bodies (2) and the add-on housing bodies (3a, 3b), and also the arrangements of the swivelling bodies (17a, 17b) on the associated add-on housing bodies (3a, 3b) are each arranged mirror-symmetrically with respect to a centre plane (11) of the main housing body (2) extending between the cylinder drums (13a, 13b) at right angles to their common axis of rotation (21).
  10. Hydrostatic machine according to one of the preceding claims, characterised in that the swivelling bodies (17) and the cylinder drums (13a, 13b) are arranged in housing chambers (4a, 4b) and are mountable and demountable through housing openings closed by the add-on housing bodies (3a, 3b).
  11. Hydrostatic machine according to one of the preceding claims, characterised in that one of the two add-on housing bodies (3a, 3b) is a one-piece or two-piece part of the housing (2c) of a third unit (E3).
  12. Hydrostatic machine according to Claim 11, characterised in that the third unit (E3) is formed by a piston machine (5c), in particular an axial piston machine, or a gear machine.
  13. Hydrostatic machine according to Claim 12, characterised in that the axial piston machine (5c) has a swash plate (17a, 17b) which is mounted on the side of the add-on housing body (3b) facing away from the main housing body (2).
  14. Hydrostatic machine according to Claim 13, characterised in that circular-segment-shaped concave bearing surfaces (18a) for a swivelling body (17c) of the piston machine (5c) of the third hydraulic unit (E3) are arranged on the side of the add-on housing body (3b) facing away from the main housing body (2).
  15. Hydrostatic machine according to one of Claims 11 to 14, characterised in that the third unit (E3) is mounted on an extension (45) of the drive shaft (7b) of the adjacent second hydrostatic unit (E2) or is mounted on a separate drive shaft (7c), the inner end of which is mounted on the associated add-on housing body (3b).
  16. Hydrostatic machine according to Claim 15, characterised in that a common rotary bearing (61) for the drive shaft (7b) of the second hydrostatic unit (E2) and for the drive shaft (7c) of the third unit (E3) is formed on the add-on housing body (3b).
  17. Hydrostatic machine according to one of the preceding claims, characterised in that the direction of rotation of the hydrostatic machine (1) is reversible by exchanging the control bodies (25a, 25b).
EP01905687A 2000-05-03 2001-01-25 Hydrostatic machine Expired - Lifetime EP1278960B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10021485 2000-05-03
DE10021485A DE10021485B4 (en) 2000-05-03 2000-05-03 Hydrostatic machine
PCT/EP2001/000819 WO2001083988A1 (en) 2000-05-03 2001-01-25 Hydrostatic machine

Publications (2)

Publication Number Publication Date
EP1278960A1 EP1278960A1 (en) 2003-01-29
EP1278960B1 true EP1278960B1 (en) 2006-05-17

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Family Applications (1)

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EP01905687A Expired - Lifetime EP1278960B1 (en) 2000-05-03 2001-01-25 Hydrostatic machine

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US (1) US6846165B2 (en)
EP (1) EP1278960B1 (en)
JP (1) JP2003532025A (en)
DE (2) DE10021485B4 (en)
WO (1) WO2001083988A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107781125A (en) * 2016-08-31 2018-03-09 浙江工业大学 Float type two dimension double crosslinking piston pump

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005037618A1 (en) * 2005-05-20 2006-11-23 Brueninghaus Hydromatik Gmbh Hydrostatic piston machine according to the floating cup concept
DE202010006498U1 (en) * 2010-05-05 2010-08-19 Lincoln Gmbh Lubricant pump and machine with such a lubricant pump
US9074670B1 (en) 2011-05-27 2015-07-07 Hydro-Gear Limited Partnership Hydraulic pump assembly
DE102013208453A1 (en) 2013-05-08 2014-11-13 Robert Bosch Gmbh Hydrostatic double pump, in particular axial piston double pump in swash plate design
CN103696920B (en) * 2013-12-08 2016-08-17 沃尔科技有限公司 Shaft coupling high-pressure plunger pump
JP7285768B2 (en) * 2019-12-16 2023-06-02 株式会社クボタ Housing structure
JP2022022528A (en) * 2020-06-25 2022-02-07 株式会社クボタ Hydraulic mechanism

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR629542A (en) 1927-02-21 1927-11-12 Double acting valveless pump for artificial silk spinning and other applications
US2371974A (en) * 1941-03-11 1945-03-20 Alfons H Neuland Fluid engine
DE1075915B (en) * 1954-10-14 1960-02-18 Chr Knoedler & Soehne Hydrostatic transmission
US3996841A (en) * 1971-02-23 1976-12-14 Sundstrand Corporation Hydraulic pump or motor
US4041843A (en) * 1976-03-15 1977-08-16 Vladimir Petrovich Mischenko Axial-piston variable-delivery pump with valve directional control of pressure fluid
GB1487542A (en) * 1976-03-30 1977-10-05 Vnii Pk I Promy Gidroprivodov Axial-piston variable-delivery pump and hydraulic drive
DE3041832A1 (en) * 1980-11-06 1982-05-13 Karl Dipl.-Ing. 7000 Stuttgart Schlecht COAXIAL DOUBLE PUMP
US4624175A (en) * 1985-08-28 1986-11-25 Wahlmark Gunnar A Quiet hydraulic apparatus
JPH02105580U (en) * 1989-02-10 1990-08-22
JPH0612275Y2 (en) * 1989-12-13 1994-03-30 株式会社神崎高級工機製作所 Fixed swash plate for HST transmission
DE4225380B4 (en) * 1992-07-31 2004-07-15 Linde Ag Hydrostatic unit with a main pump and a secondary pump
JP2602922Y2 (en) * 1993-12-28 2000-02-07 カヤバ工業株式会社 Double pump
US5540563A (en) * 1994-09-16 1996-07-30 Sauer Inc. Unitary housing for double hydraulic unit
KR100221591B1 (en) 1997-03-22 1999-09-15 토니헬 Auxiliary pump structure
DE19736160A1 (en) * 1997-08-20 1999-02-25 Bosch Gmbh Robert High pressure fuel pump for IC engine in common rail systems
DE19828180C2 (en) 1998-06-24 2000-04-20 Brueninghaus Hydromatik Gmbh Double pump unit

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107781125A (en) * 2016-08-31 2018-03-09 浙江工业大学 Float type two dimension double crosslinking piston pump
CN107781125B (en) * 2016-08-31 2019-05-28 浙江工业大学 Float type two dimension double crosslinking piston pump

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US6846165B2 (en) 2005-01-25
WO2001083988A1 (en) 2001-11-08
EP1278960A1 (en) 2003-01-29
DE50109818D1 (en) 2006-06-22
DE10021485B4 (en) 2006-03-23
US20030077189A1 (en) 2003-04-24
JP2003532025A (en) 2003-10-28
DE10021485A1 (en) 2001-11-15

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