EP1882855A2 - Hydraulic motor - Google Patents

Abstract

The motor (1) has a motor connecting piece connected with a housing in a torque proof manner and another motor connecting piece (20) connected with a rotor (10) in a torque proof manner. The rotor is axially and radially supported in the housing over axial and radial friction bearing surfaces (28 - 31). The motor connecting piece (20) connected with the rotor is supported in the housing over the axial and radial friction bearing surfaces.

Description

The present invention relates to a hydraulic rotary motor, in particular a slewing gear for a hoist such as excavator gripper, etc., with a housing in which a rotor is rotatably received, and an annular piston with an inner and an outer toothing, which sits between the rotor and the housing , so that between the annular piston and an external toothing of the rotor and / or an internal toothing of the housing filled with pressurized fluid displacement chambers are formed, wherein a first motor connecting piece rotatably connected to the housing and a second motor connecting piece rotatably connected to the rotor.

Such a hydraulic rotary motor is from the DE 33 42 131 A1 known. Also the DE 37 29 049 C1 , the DE 2 365 057 or the DE 196 05 879 A1 show hydraulic rotary motors of this type, in which an annular piston rotates wobbling and cooperates with an internal toothing on the housing and an external toothing on the rotor in order to drive the rotor in rotation relative to the housing. Usually, such rotary motors are used as slewing gear for hoists of excavators, general cargo cranes or timber cranes, wherein when used for example for an excavator gripper, the first housing-mounted motor connector is connected to the excavator handle, while on the second, connected to the rotor motor connector of the excavator gripper is mounted. About the rotational movement of the rotor relative to the housing of the excavator gripper can be rotated in a conventional manner against the excavator handle.

In such hydraulic rotary motors of the type mentioned above, the rotor usually sits non-rotatably, but longitudinally displaceable on a drive shaft whose emerging from the housing end forms the second motor connector for attachment of the hoist. In order to absorb the forces and moments introduced by the hoist onto the motor, the motor shaft is supported on both sides of the rotor via tapered roller bearings on the housing. This shows z. B. the DE 33 42 131 or the DE 37 29 049 , As a result, axial forces and bending moments introduced into the motor shaft should be largely kept away from the rotor, so that it can run smoothly and precisely in the annular housing gap in which the annular piston is received and the sealing of the displacement chambers is not adversely affected by bearing and reaction forces on the rotor experiences. However, a disadvantage of this bearing of the motor shaft via tapered roller bearings is the resulting large axial length of the motor. In addition, there are static over-determinations, since in addition to the shaft bearing the rotor itself must be precisely guided so that the displacement chambers do not experience excessive leakage. In addition, the production and assembly costs through the corresponding components is relatively high.

Here, the present invention seeks to remedy this situation. It is the object of the invention to provide an improved rotary motor of the type mentioned, which avoids the disadvantages of the prior art and the latter develops in an advantageous manner. Preferably, a structurally simple, compact and axially kurzbauender rotary motor is to be created, which is inexpensive to produce by low production costs and material use.

This object is achieved by a hydraulic rotary motor according to claim 1. Preferred embodiments of the invention are the subject of the dependent claims.

In the rotary motor according to the invention is dispensed with a separate support of the motor shaft through the known tapered roller bearings. Rather, the forces and torques introduced by the motor connecting piece connected to the respective hoisting device are intercepted directly via the rotor itself. According to the invention, the rotor is axially and radially supported on the housing via slide bearings. The second motor connection piece connected to the rotor for fastening the hoist is supported on the housing via the rotor and the plain bearings that support it. By dispensing with separate shaft bearings in the form of tapered roller bearings or other bearings and the interception of forces and moments on the rotor itself and corresponding bearings free of bearings can on the one hand, the axial length of the motor be considerably shortened. On the other hand, the production costs and the use of materials reduced by the elimination of the separate bearings for the motor shaft, which cost savings can be achieved. In particular, the second motor connecting piece connected to the rotor can be rigidly connected to the rotor and can be supported exclusively via the plain bearings acting on the rotor.

In a further development of the invention, the rotor can be rigidly seated on an output shaft whose end emerging from the housing forms the second motor connecting piece for fastening the hoist. The rotor can be pressed onto the output shaft or connected in another suitable manner rigidly thereto.

In order to achieve a particularly compact arrangement, can be dispensed with a motor shaft entirely. The rotor itself replaces the motor shaft and itself forms the motor connection piece for fastening the hoist, which advantageously can be fastened directly to the rotor. The rotor can for this purpose suitable fastening means, in particular bores for receiving Bolt for attaching the hoist, have. Conveniently, the rotor has a stubby neck whose end face forms the mounting surface for the hoist.

Advantageously, the rotor forms a ring in whose inner recess a rotary brake, preferably a multi-disc brake, can be arranged. As a result, on the one hand a particularly compact arrangement is achieved. On the other hand, the braking forces can be introduced directly from a housing section in the rotor, which is particularly suitable for this purpose by its high-strength material.

In a further development of the invention, the rotor may have a disc section which has on opposite sides two Axialgleitlagerflächen with which the rotor is supported axially in opposite directions in a housing gap into which the annular piston is also used. In addition, the rotor may have two shaft sections which protrude from both sides of the said disk section axially in the manner of a hollow shaft stub. At these shaft sections radial sliding bearing surfaces are provided in a further development of the invention, with which the rotor is supported at the edges of the housing gap. In this way, a stiff support of the rotor can be achieved both with respect to axial forces and radial forces and corresponding moments.

Basically, the sliding bearing surfaces can be formed by bearing inserts, which are used on the housing side and / or rotor side. In a further development of the invention, however, the sliding bearing surfaces are formed directly by the material or the surface of the rotor and of the housing section adjacent thereto. If the housing is made of gray cast iron, good sliding bearing properties can be achieved directly by the housing material.

Advantageously, the bearing of the rotor dispenses with the conventional distributor or pressure plates, which are movably guided in the housing and, for example, from the construction according to DE 33 42 131 are known. As a result, the production cost and material usage can be further reduced.

In order to ensure adequate lubrication of the sliding bearing of the rotor, according to a further aspect of the invention, a Ölleit- and / or channel system is provided in particular in the housing, which hydraulic oil from the displacement chambers and / or from the pressure supply channels of the engine to the bearing points of the rotor and / or the associated drive shaft passes. In particular, can be provided to improve the oil supply of the sliding bearing surfaces connecting channels to the pressure channels through which the displacement chambers of the engine filled with oil and the motor is ultimately driven. However, the oil supply of the bearings via a channel system in the housing, which conducts hydraulic oil from the displacement chambers and / or from the pressure supply channels of the engine to the bearings, but also has considerable advantages in the lubrication of conventionally mounted on roller bearings rotors or drive shafts of such engines. According to an advantageous embodiment of the invention can be provided in particular in the radial sliding bearing surfaces of the rotor or the corresponding radial sliding bearing surfaces of the housing annular grooves, which are each connected to one of the pressure channels for supplying the displacement chambers. The respective annular groove ensures the distribution of the oil over the entire circumference. In order to use the oil pressure applied by the pressure ducts also for the lubrication of the axial sliding bearing surfaces, transverse bores can be provided in the housing which connect the said axial sliding bearing surfaces to one of the aforementioned annular grooves. Alternatively or additionally, oil holes could also lead directly from the pressure channels to supply the displacement chambers on the Axialgleitlagerflächen.

Advantageously, in the housing, a first set of oil supply channels, which are connected to a pressure channel for supplying the positive displacement chambers, and a second set of oil supply channels, which are connected to a pressure channel for supplying the displacement chambers for clockwise rotation.

For this purpose, two annular grooves may be formed in superimposed planes in the housing and each have a wavy or serpentine contour, wherein the wavy or serpentine contours of the two annular grooves are arranged offset from one another. As a result, the annular grooves can be drilled individually through the feed holes in the bulges without the respective other annular groove would be mitverbunden. The wave-shaped formation can advantageously be accomplished by casting technology, for example. By inserting correspondingly shaped tubular cores.

Alternatively or additionally, it is advantageously possible to use approximately tubular insert sleeves with feed openings which are open to one annular channel in each case in the feed bores connected to the annular channel. Here, the feed holes can penetrate both annular grooves, so that can be dispensed with a wave or serpentine annular channel contour.

The at least one annular groove may be formed open towards an inner circumferential surface of the housing, on which the rotor and / or the drive shaft connected thereto is radially mounted, in order to ensure lubrication at this bearing point.

Alternatively, the annular groove can also be formed completely closed inside the housing and connected via feed bores with at least one bearing of the rotor and / or the drive shaft connected thereto.

It has proven to be particularly advantageous for the lubrication of the axial sliding bearing surfaces if transverse bores are provided in the toothed projections of the rotor which open onto the axial sliding bearing surfaces of the rotor. As a result, oil can flow from one side of the rotor to the other to ensure a sufficient supply of oil on both sides of the teeth of the rotor on which the Axialgleitlagerflächen are provided.

In a further development of the invention can be formed in the Axialgleitlagerflächen of the rotor plate-shaped depressions that form pressure pockets or better distribute the oil located there. In particular, these plate-shaped depressions are arranged on the side of the rotor, which intercepts the tensile forces introduced by the hoist. The plate-shaped depressions are advantageously in connection with the transverse bores in the toothed projections of the rotor, so that they are fed from the other side of the rotor forth with oil.

In order to introduce sufficient oil into the aforementioned transverse bores in the toothed projections of the rotor, distributor grooves can be provided in the axial slide bearing surfaces with the transverse bores, these distributor grooves being arranged in particular on the side of the rotor opposite the aforementioned plate-shaped depressions.

To ensure a circulating oil pressure and thus an oil exchange by circulating pressure differences in the radial sliding bearing surfaces can be provided in the invention in the radial sliding bearing surfaces of the housing and / or the rotor and / or the associated shaft axial grooves for oil distribution, in particular offset by 180 ° be.

Advantageously, a Ölleit- or channel system is also provided for the lubrication of the annular piston for this. In order to convey the oil to the axial surfaces of the annular piston, the annular piston thickness may decrease toward the edges of the external teeth, wherein bevels, for example in the form of a chamfer, may be provided towards the external teeth in particular at the edges of the axial sliding bearing surfaces of the annular piston. This makes it easier for the oil to get onto the sliding bearing surfaces of the annular piston. The outwardly conical shape of the piston also ensures floating and centering of the annular piston. Furthermore, parallelism and angle errors have a smaller effect.

Fig. 1:

eine schematische Schnittansicht durch einen Drehmotor nach einer ersten bevorzugten Ausführung der Erfindung, bei der der in dem Gehäuse aufgenommene Rotor des Motors selbst das mit einem Hebezeug verbindbare Motoranschlussstück bildet,

Fig. 2:

eine schematische Schnittansicht eines hydraulischen Drehmotors nach einer alternativen Ausführung der Erfindung, bei der das Motoranschlussstück zur Befestigung eines Hebezeugs von einer Motorwelle gebildet wird, mit der der Rotor starr verbunden ist,

Fig. 3:

eine schematische Draufsicht auf den Ringkolben mit Innen- und Außenverzahnung und den damit zusammenwirkenden Rotor und das damit zusammenwirkende Gehäuse der Drehmotoren aus Fig. 1 und 2,

Fig. 4:

einen Axialschnitt durch den Rotor der Drehmotoren aus Fig. 1 und 2, der die Querbohrungen in den Verzahnungsnasen zur Ölversorgung der Gleitlagerflächen zeigt,

Fig. 5:

eine Draufsicht auf die Verzahnungsnasen des Rotors und die darin eingebrachten Verteilernuten und die damit verbundenen Querbohrungen,

Fig. 6:

eine Draufsicht auf die im Vergleich zur Fig. 5 gegenüberliegende Seite der Verzahnungsnasen des Rotors, die die darin eingebrachten tellerartigen Vertiefungen und die damit verbundenen Querbohrungen zeigt,

Fig. 7:

einen Axialschnitt durch den Ringkolben der Motoren aus den Figuren 1 und 2, der die zu der Außenkontur des Ringkolbens abnehmende Ringkolbendicke zeigt,

Fig. 8:

eine Schnittansicht entlang der Linie A-A in Fig. 2, die im Lagerdeckel des Gehäuses ausgebildete Schmiernuten zeigt,

Fig. 9:

eine Schnittansicht des Drehmotors nach Fig. 2, die eine Entlastungsbohrung zwischen einer Axiallagerfläche der Motorwelle und einem Leckölraum zwischen dem Ringkolben und dem Gehäuse zeigt,

Fig. 10:

eine Schnittansicht des Gehäuses im Bereich eines Druckkanals zur Speisung der Verdrängungskammern für eine Drehrichtung, die einen Ringverteilerkanal in dem Gehäuse und damit in Verbindung stehende Öleinspeisekanäle zeigen, in die hülsenförmige Einsätze mit Einspeisebohrungen eingesetzt sind,

Fig. 11:

eine Schnittansicht des Gehäuses ähnlich Fig. 10 entlang der Linie A-A in Fig. 13, wobei bei der Ausführung nach Fig. 11 die in übereinanderliegenden Ringverteilerkanäle jeweils versetzt wellenförmig ausgebildet sind, so dass die Ölspeisebohrungen direkt in den jeweiligen Ringverteilerkanal hinein angebohrt werden können,

Fig. 12:

einen ausschnittsweisen Axialschnitt durch den Gehäusedeckel, der die Lage der Ringverteilerkanäle aus Fig. 11 und die Verbindung des unteren Ringverteilerkanals über eine Speisebohrung mit der Axialgleitlagerfläche des Rotors zeigt,

Fig. 13:

einen ausschnittsweisen Axialschnitt des Gehäuses ähnlich Fig. 12, der die Verbindung des oberen Ringverteilerkanals mit der Axialgleitlagerfläche am Rotor zeigt,

Fig. 14:

eine schematische Schnittansicht des Gehäuses mit einem Ringverteilerkanal nach einer alternativen Ausführung der Erfindung, der zur Innenausnehmung des Gehäuses hin nicht offen ist, wodurch entsprechende Dichtungen nicht mehr erforderlich sind,

Fig. 15:

eine schematische Schnittansicht eines Drehmotors ähnlich Fig. 2, wobei hier die Ölversorgung der Gleitlagerflächen für den Rotor bzw. die Welle aus einem Druckkanal zur Druckversorgung des an den Drehmotor anschließbaren Hebezeugs gespeist wird, und

Fig. 16:

eine schematische Schnittansicht eines Drehmotors ähnlich Fig. 15, wobei hier die bei vom Hebezeug eingeleiteten Zugkräften belastete Rotorseite mit Drucköl aus dem Druckversorgungskanal gespeist wird, der zur Versorgung des an den Drehmotor anbaubaren Hebezeugs vorgesehen ist.

The invention will be explained in more detail with reference to preferred embodiments and associated drawings. In the drawings show:

Fig. 1:

a schematic sectional view through a rotary motor according to a first preferred embodiment of the invention, in which the accommodated in the housing rotor of the motor itself forms the connectable with a hoist motor connector,

Fig. 2:

a schematic sectional view of a hydraulic rotary motor according to an alternative embodiment of the invention, in which the motor connecting piece for attaching a hoist is formed by a motor shaft to which the rotor is rigidly connected,

3:

1 is a schematic plan view of the annular piston with internal and external teeth and the rotor interacting therewith and the housing of the rotary motors cooperating therewith from FIGS. 1 and 2;

4:

an axial section through the rotor of the rotary motors of Figures 1 and 2, which shows the transverse bores in the Verzahnungsnasen for oil supply of the sliding bearing surfaces,

Fig. 5:

a plan view of the gear teeth of the rotor and the distribution grooves introduced therein and the transverse bores connected thereto,

Fig. 6:

a plan view of the opposite in comparison to FIG. 5 side of the teeth of the teeth of the rotor, which shows the dish-like depressions introduced therein and the transverse bores connected thereto,

Fig. 7:

an axial section through the annular piston of the motors of Figures 1 and 2, which shows the decreasing to the outer contour of the annular piston ring piston thickness,

Fig. 8:

3 is a sectional view along the line AA in Fig. 2, showing the lubrication grooves formed in the bearing cap of the housing,

Fig. 9:

2 is a sectional view of the rotary motor according to FIG. 2, showing a relief bore between an axial bearing surface of the motor shaft and a leakage oil space between the annular piston and the housing;

Fig. 10:

a sectional view of the housing in the region of a pressure channel for feeding the displacement chambers for one direction of rotation, showing a ring distribution channel in the housing and related oil feed channels are inserted into the sleeve-shaped inserts with feed bores,

Fig. 11:

a sectional view of the housing similar to FIG. 10 along the line AA in FIG. 13, wherein in the embodiment according to FIG. 11, the annular distribution channels arranged one above the other are wave-shaped, so that the oil feed bores can be drilled directly into the respective annular distribution channel,

Fig. 12:

a fragmentary axial section through the housing cover, showing the position of the annular distribution channels of FIG. 11 and the connection of the lower annular distribution channel via a feed bore with the axial sliding bearing surface of the rotor,

Fig. 13:

a partial axial section of the housing similar to FIG. 12, showing the connection of the upper annular distribution channel with the Axialgleitlagerfläche on the rotor,

Fig. 14:

a schematic sectional view of the housing with a ring distribution channel according to an alternative embodiment of the invention, which is not open to the inner recess of the housing, whereby corresponding seals are no longer required,

Fig. 15:

a schematic sectional view of a rotary motor similar to Figure 2, in which case the oil supply of the sliding bearing surfaces for the rotor or the shaft is fed from a pressure channel for supplying pressure to the rotary motor can be connected to the hoist, and

Fig. 16:

a schematic sectional view of a rotary motor similar to FIG. 15, in which case the rotor side loaded with the pulling forces introduced by the hoisting gear is supplied with pressure oil from the pressure supply channel, which is provided for supplying the hoist which can be mounted on the rotary motor.

The rotary motor 1 shown in Fig. 1 comprises a substantially cup-shaped housing 2, which consists in the illustrated embodiment substantially of three parts, namely the motor head 3, the rotor housing ring 4 and the bearing cap 5. As shown in Fig. 1, the bearing cap 5 set on the rotor housing ring 4 and screwed by screw 6 with the radially projecting flange 7 of the engine head 3, so that between the bearing cap 5 and the engine head 3, an annular rotor gap 8 is formed. In the mentioned rotor gap 8 of the annular piston 9 is received and radially within this annular piston 9 of the substantially also disc-shaped rotor 10. More specifically, a disc portion 11 of a rotor / shaft unit fits snugly between the bearing cap 5 and the engine head 3. On both sides of the disc portion 11 projecting are integrally formed on the latter shaft portions 12 and 13, which run with its outer circumference fit on inner peripheral surfaces of the bearing cap 5 and the engine head 3.

As shown in FIG. 3, the annular piston 9 is provided with an internal toothing 14 and an external toothing 15 and cooperates with these on the one hand with an outer toothing 16 of the rotor 10 and on the other hand with an internal toothing 17 of the rotor housing ring 4 in a conventional manner. By Druckfluidbeaufschlagung between the annular piston 9 and the rotor 10 and the rotor housing ring 4 formed displacement chambers 18, the annular piston 9 can be driven wobbling circumferentially, causing it on the teeth of the rotor 10 relative to the rotor housing ring 4 and thus the housing 2 drives, as described in detail in the DE 33 42 131 A1 to which reference is made in this regard.

As shown in FIG. 1, the rotary motor according to this embodiment of the invention completely dispenses with a separate motor shaft, which is replaced by the rotor 10. The end face 19 of the shaft portion 13 of the rotor 10 emerging from the housing 2 forms a motor connection piece 20, to which a hoist 21, such as, for example, an excavator gripper, can be mounted. For this purpose, 10 bolts 22 are provided in the rotor. The other motor terminal 23 is formed in a conventional manner by the motor head 3 of the housing 2, with which the rotary motor 1 can be grown, for example, to the stem of an excavator.

As Fig. 1 further shows, the rotor 10 is formed as a ring. In the hollow interior 24 of the rotor 10, a rotary brake 25 is arranged in the form of a multi-disc brake, which does not extend axially beyond the rotor and ensures a particularly compact design of the engine. The inner peripheral surface of the rotor 10 supports, for example via a splined shaft a set of the slats of the rotary brake 25, the other set of slats rotatably mounted rotatably on a sleeve-shaped driving piece 26, which is itself also rotationally fixed to the housing 2. About a brake piston 27 in the space between said driver piece 26 and the rotor 10, the slats of the rotary brake 25 can be pressed against each other and thereby the braking effect can be brought about.

As shown in FIG. 1, the rotary motor 1 completely dispenses with roller bearings. The introduced from the hoist 21 forces and moments are intercepted only by the rotor 10 itself and this on the housing 2 supporting plain bearings. For this purpose, the rotor 10 comprises, on the one hand, axial sliding bearing surfaces 28 and 29 which are formed by the opposite flat sides of the disk section 11 of the rotor 10 become. On the other hand, the rotor 10 includes radial sliding bearing surfaces 30 and 31 formed by the outer peripheral surfaces of the shaft portions 12 and 13 of the rotor 10. It is understood that corresponding sliding bearing surfaces are provided on the housing 2, which cooperate with said axial sliding bearing surfaces 28 and 29 and radial sliding bearing surfaces 30 and 31.

Also in the embodiment of the rotary motor 1 shown in Fig. 2 is dispensed rolling bearings. Again, the introduced from the hoist 21 forces and moments are intercepted exclusively via plain bearings. In particular, here too the rotor 10 is mounted axially on the housing 2 via axial sliding bearing surfaces 28 and 29 on the flat sides of its disk section 11. In contrast to the embodiment of FIG. 1, however, the annular rotor 10 is pressed onto a drive shaft 32 in this embodiment. The rotor 10 is rigidly connected to the drive shaft 32, so that both axial forces and bending moments and radial forces are introduced from the drive shaft 32 in the rotor 10 and vice versa intercepted by the latter. The radial sliding bearing surfaces 30 and 31 are provided in the embodiment of FIG. 2 at the shaft portions 12 and 13 of the drive shaft 32, which connect axially to the rotor 10. Since in the embodiment of FIG. 2, the rotor 10 is seated on the drive shaft 32, not the rotor 10 itself forms the motor connector for the attachment of the hoist. The motor connection piece 20 is formed by the end face 19 of the end of the drive shaft 32 emerging from the housing 2 (cf., FIG. 2).

For oil supply of the axial and radial sliding bearing surfaces 28, 29, 30 and 31, various oil passages are formed in the rotor 10 and in the housing 2, through which the oil is conducted in sufficient quantity to said slide bearing surfaces.

First, such channels are provided in the rotor 10 to have sufficient oil on both Axialgleitlagerflächen 28 and 29. As shown in FIG. 4, 10 transverse bores 34 are provided in the teeth 33 of the rotor, which connect the Axialgleitlagerfläche 28 on the upper side of the rotor 10 with the Axialgleitlagerfläche 29 on the underside of the rotor 10. This can be done from the top of the rotor 10 oil are led to the lower bearing surface. In addition, a pressure equalization or a higher pressure on the lower thrust bearing surface 29 can be generated, whereby to some extent the operating loads are compensated, which are initiated by tensile forces on the hoist 21.

As shown in FIG. 5, 10 distribution grooves 35 are provided in the Axialgleitlagerfläche 28 on the upper side of the rotor, which extend approximately tangentially to the circumferential direction and are connected to the aforementioned transverse bores 34. This improves a continuous flow of oil to the lower bearing and a corresponding pressure build-up. In a further development of the invention, the distributor grooves 35 are designed to be very narrow so that the axial pressure remains low. The width of the distributor grooves 35 may be less than 1 mm.

On the side opposite the distributor grooves 35, the transverse bores 34 passing through the toothed projections 33 open into plate-like recesses 36, as shown in FIG. 6. These large pressure pockets improve the lubrication of the lower thrust bearing surface 29 and can support or ensure a sliding of the rotor 10 relative to the bearing cap 5, even at higher operating loads. The thrust bearings can thereby be hydraulically counter to the main force direction, i. the introduced via the hoist 21 tensile forces are relieved.

By supplying oil to the Axialgleitlagerflächen 28 and 29 from the inside over said transverse bores 34, it is possible to form the outer contour of the rotor 10 and the inner contour of the annular piston 9 without chamfers or other bevels. Such chamfers or slight chamfers to the pressure chamber would also ensure a pressure supply of the sliding bearing surfaces 28 and 29 and ensure a certain slipping of the rotor 10 and the annular piston 9 in the oil bath. On the other hand, this leads to a leakage in the chamber area, which is avoided in the Scharfkantenausbildung. Nevertheless, the internal supply of the axial sliding bearing surfaces 28 and 29 via the transverse bores 34 ensures that a tearing off of the oil film does not occur.

Advantageously, the slide bearing surfaces 28 and 29 are fed via feed bores from pressure channels, which are provided either to supply pressure to the displacement chambers 18 or to supply pressure to a mounted hoist in the housing 2. For this purpose, in an advantageous manner, as shown in Figures 10 to 14, in the engine head 3 ring manifold channels 37 and 38 may be introduced, which are arranged at different height level and connected to one of the oil supply channels for each direction of rotation. As FIGS. 12 and 13 show, feed bores 39 and 40 lead from the ring distributor passages 37 and 38 onto the axial sliding bearing surface 28. The oil guided there can then be transferred, as described above, over the transverse bores 34 formed in the toothed projections 33 to the opposing axial sliding bearing surface 29 be guided.

As shown in FIG. 10, the ring manifolds 37 to 38 on the inner peripheral surface of the housing 2 supporting the radial slide bearing surface 30 of the rotor 10 may be open toward the inside so that they can be machined and ensure lubrication of the radial slide bearing surfaces therein , Each second of the feed bores 39 to 40 can be connected by tapping with the respective annular distribution channel 37 and 38, respectively. In this case, first the feed bores 39 and 40 can be drilled through or in both annular distribution channels 37 and 40 and then sleeve-shaped inserts 50 are inserted into the feed holes, which have a Einspeisbohrung in each matching height and thus the respective feed channel 39 and 40 with the desired ring distribution channel Connect 37 or 38, cf. Fig. 10.

FIG. 11 shows an alternative embodiment of the annular distributor channels 37 to 38. Here, each annular distributor channel 37 or 38 is cast in such a way that the feed bore 39 to 40 can be drilled directly offset from the respective other channel. This is shown in section in FIG. 12 or FIG. 13. As FIG. 11 shows, the two channels each have an offset wave contour with respect to one another, so that a respective one of them has a wave contour Bulge 51 of a ring manifold 37 can be drilled without hitting the other ring distribution channel 38.

As an alternative to the inwardly open design, the annular distribution channels 37 and 38, as shown in FIG. 14, may also be formed completely closed in the interior of the housing 2, eg. B. by a suitable casting technique. This has the advantage that on the inner peripheral surface of the housing 2 no seals must be provided. Again, the annular distribution channels 37 and 38 are advantageously wave-shaped and drilled directly, so that the feed holes 39 and 40 communicate with the respective ring distribution channel 37 or 38.

Alternatively or additionally, lubrication of the sliding bearing surfaces can also take place from the pressure channel 41 in the housing 2, which is provided for the pressure supply of the hoist 21 attached to the rotary motor 1. As FIG. 15 shows, a pressure line 42 can, for example, act on an annular space between the housing and the drive shaft 32, which thus acts as a piston, as it were, and effects a pressure relief. Preferably, the pressure line 42 is connected to the shooting force pressure line 41, so that when closing force is applied, the pressure relief is ensured.

As FIG. 9 shows, an oil supply of the slide bearing surfaces can also be effected from the leakage oil chamber 43, which is formed between the annular piston 9 and the rotor housing ring 4. Advantageously, the leakage oil chamber 43 is subjected to a relatively low pressure, which actually serve to foam the oil and can be accomplished via control valves, but advantageously also ensures lubrication.

Advantageously, in the inner peripheral surfaces of the bearing cap 5 and / or the engine head 3, which receive the shaft portions 12 and 13 of the rotor 10 and the drive shaft 32, axial grooves 44 offset by 180 ° to each other.

In this way, it can be achieved that oil circulation in the radial sliding bearing surfaces 30 and 31 takes place due to the circulating oil pressure.

In order to achieve a lubrication of the annular piston 9, can be provided in an advantageous development of the invention, as shown in Figure 7, that the thickness of the annular piston 9 decreases towards the outer contour. Corresponding flattening or chamfering 45 ensures that oil from the leakage oil space 43 can be distributed on the upper or lower side of the annular piston 9. The annular piston 9 floats, so to speak, and is sufficiently lubricated on its top and bottom. In addition, parallelism or angle errors have less effect.

Claims (21)

Hydraulic rotary motor, in particular slewing gear for a hoist such as excavator gripper, etc., with a housing (2) in which a rotor (10) is rotatably received, and an annular piston (9) with an internal toothing (14) and an external toothing (15), which sits between the rotor (10) and the housing (2), so that between the annular piston (9) and an external toothing (16) of the rotor (10) and / or an internal toothing (17) of the housing (2) displacement chambers (18 ), wherein a first motor connecting piece (23) is non - rotatably connected to the housing (2) and a second motor connecting piece (20) is connected in a rotationally fixed manner to the rotor (10), characterized in that the rotor (10) is guided via plain bearings (28, 29 , 30, 31) is supported axially and radially on the housing (2) and the second motor connection piece (20) connected to the rotor (10) is supported on the housing (2) exclusively via the slide bearings (28, 29, 30, 31) , A rotary motor according to the preceding claim, wherein the rotor (10) is rigidly seated on a drive shaft (32) whose end emerging from the housing (2) forms the second motor connecting piece (20). A rotary motor according to claim 1, wherein the rotor (10) itself constitutes the second motor fitting (20). A rotary motor according to one of the preceding claims, wherein the rotor (10) forms a ring. Rotary motor according to one of the preceding claims, wherein in an inner recess (24) of the rotor (10) a rotary brake (24), in particular a multi-disc brake, is arranged. A rotary motor according to one of the preceding claims, wherein the rotor (10) has a disc portion (11) having on opposite sides two Axialgleitlagerflächen (28, 29) with which the rotor (10) in a housing gap (8) is supported, in which also the annular piston (9) is arranged, and wherein on the disc portion (11) on both sides axially projecting shaft portions (12, 13) of the rotor (10) and / or a rigidly connected drive shaft (32) Radialgleitlagerflächen (30, 31) , with which the rotor (10) is supported at the edges of the housing gap (8). Rotary motor according to the preamble of claim 1 and / or according to one of the preceding claims, wherein in the housing (2) oil supply channels (37, 38, 39, 40) are provided for the bearing points of the rotor (10), from a pressure channel for supply the displacement chambers (18) are fed. A rotary motor according to the preceding claim, wherein in the housing (2) a first oil supply channel or set of oil supply channels (38, 40) provided with a pressure channel for supplying the displacement chambers (18) for Linkslauf is connectable, and a second oil supply channel or set of oil supply channels (37, 39) which is connectable to a pressure channel for supplying the displacement chambers (18) for clockwise rotation are provided. Rotary motor according to one of the preceding claims, wherein in the housing (2) at least one annular groove (37, 38) is provided, which is connected to one of the pressure channels for supplying the displacement chambers (18). Rotary motor according to the preceding claim, wherein the at least one annular groove (37, 38) via feed bores (39, 40) is connected to at least one Axialgleitlagerfläche (28). Rotary motor according to one of the preceding claims, wherein the at least one annular groove (37, 38) is open towards an inner peripheral surface of the housing (2), on which the rotor (10) and / or the associated drive shaft (32) is radially mounted , Rotary motor according to one of claims 9 or 10, wherein the at least one annular groove (37, 38) formed completely closed inside the housing (2) and via feed bores with at least one bearing of the rotor (10) and / or the associated drive shaft (32 ) connected is. Rotary motor according to one of the preceding claims, wherein two annular grooves (37, 38) are arranged in superimposed planes and each having a wavy or serpentine contour, wherein the wavy or serpentine contours of the two annular grooves (37, 38) are arranged offset to each other. Rotary motor according to one of the preceding claims, wherein in the feed bores preferably about tubular inserts (50) are used with each to an annular channel (37, 38) open feed openings. Rotary motor according to one of the preceding claims, wherein in the Verzahnungsnasen (33) of the rotor (10) transverse bores (34) are provided, which open on the Axialgleitlagerflächen (28, 29) of the rotor (10). Rotary motor according to one of the preceding claims, wherein in the Axialgleitlagerflächen (28, 29) of the rotor (10) plate-shaped pressure pockets are formed. Rotary motor according to one of the preceding claims, wherein in the Axialgleitlagerflächen (28, 29) with the transverse bores (34) connected distributor grooves (35) are provided. Rotary motor according to one of the preceding claims, wherein the annular piston (9) has a decreasing towards the edges of its outer toothing (15) thickness. Rotary motor according to the preceding claim, wherein bevels (45) are provided to the displacement chambers (18) at the edges of the annular piston (9). Rotary motor according to one of the preceding claims, wherein in the radial sliding bearing surfaces of the housing (2) and / or the rotor (10) and / or the associated shaft (32) Axialnuten are provided, preferably offset by 180 ° to each other. Rotary motor according to one of the preceding claims, wherein at least one compensation bore between a radial sliding bearing surface and a leakage oil space (43) between the annular piston (9) and the housing (2) is provided.

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