DE10220611A1 - rotary bearings - Google Patents

Abstract

A rotary slide bearing (25c) has an inner first bearing part (31) with an outer surface (31a) and an outer second bearing part (32) with an inner outer surface (32a). The outer bearing part (32) surrounds the inner bearing part (31). At least one roughly axially continuous first lubrication groove (38) is provided in the lateral surface (31a) of the inner first bearing part (31) and / or in the inner lateral surface (32a) of the outer second bearing part (32). In order to improve the rotary slide bearing so that it can absorb radial and axial forces and has good sliding properties, a support shoulder (42a, 42b) with a sliding surface (42c) is assigned to one of the two bearing parts (31) on one or both sides which supports the bearing part (32) axially with its side surface (32c) facing it. At least one approximately radial second lubrication groove (46a, 46b) is arranged in the sliding surface (42c) or in the side surface (32c) supported thereon. The lubrication grooves (46a, 46b, 38) are connected to each other in the area facing each other.

Description

The invention relates to a rotary slide bearing, especially for a drive shaft of an axial piston machine.

Shafts transmit torques in most cases, whereby they are mainly exposed to radial loads and are to be stored in radial bearings. It hardly occurs avoiding axial forces caused by a thrust bearing for the wave can be picked up. At a Axial piston machine becomes their drive shaft quite significant axially loaded because of the axially effective piston forces the drive shaft are transmitted. That is why the drive shaft an axial piston machine both radially and axially in to store resilient shaft bearings. Rolling bearings can do this or plain bearings. Rolling bearings are characterized by a special smooth running because of their friction loss due to the rolling friction is low. The resilience is against it of a rolling bearing is relatively small because the Surface pressure on the rolling elements is high. With one Plain bearings, on the other hand, are relatively large Sliding surface available so that the surface pressure is low can be held. Therefore plain bearings are suitable especially for large storage loads.

The friction and wear of a plain bearing to keep it low, it is known from DE 43 36 915 A1, in one of two adjacent sliding surfaces wedge-shaped Lubricant cushion to hold a lubricant to arrange. A flow of the lubricant through the Grease pillow does not take place.

The invention is based, an existing one Design the rotary slide bearing so that it is radial and axial Can absorb forces and has good sliding properties having.

This object is achieved by the features of claim 1 solved. Advantageous developments of the invention are in described the subclaims.

In the rotary slide bearing according to the invention is or are one of the two bearing parts on one or on both sides each assigned a support shoulder with a sliding surface, on the other bearing part with its the support shoulder facing side surface is axially supported. Also are radially between the bearing parts and axially between the one Bearing part and the or the adjacent support shoulders Lubrication grooves arranged, each having at least one radial lubrication groove and the at least one approximately axially running lubrication groove in the mutually facing Area areas are in connection with each other. hereby is a combined radial and axial bearing created of simple and small design is what through the combined design is achieved. It can rotary slide bearing according to the invention be designed so that it axial only in one axial direction or in both axial directions is supported and is designed as a thrust bearing. Therefore the pivot bearing according to the invention is also suitable as a so-called fixed bearing, the axial and radial forces able to absorb and in combination with an axial spaced so-called floating bearing can be arranged, the only absorbs radial forces.

Due to the presence of the invention Lubrication grooves is the rotary slide bearing according to the invention in Operation with respect to both radial and axial forces well lubricated, which reduces friction and wear and a long service life for the bearing becomes. Due to the radial or radially increasing Course of the at least one lubrication groove between the Support shoulder and the bearing part supported by him in operation when the lubrication groove is rotating Bearing part is arranged due to the lubricant effective centrifugal force an automatically effective pump or Delivery effect that causes the lubricant to radially outside of the lubrication groove and new lubricant to enter radially inside, e.g. B. by the existing Sliding joint or through a special feed opening or Supply line. From this automatic lubricant Discharge and feed not only benefits the radial extending lubrication groove, but also approximately axially extending lubrication groove when connected to the former is.

A forced delivery effect on the lubricant in the approximately axially extending lubrication groove can then reach if this lubrication groove is arranged obliquely. In doing so, she practices sliding contact with the lubricant standing sliding surface in the longitudinal direction of the Lubrication groove directed component on the Lubricant, the direction of action of the Direction of rotation and depends on whether the lubrication groove is located in the rotating or non-rotating bearing part.

The support effect already described in the area of at least one approximately radially extending lubrication groove can be forced if the lubrication groove is inclined so that the lubricant in the lubrication groove due to the Sliding contact with the sliding surface of the neighboring component is promoted to the outside in the sense of a force component. If the lubrication groove in the rotating component is arranged, it is advantageous to the lubrication groove in the the direction opposite to the direction of rotation. If on the other hand, the lubrication groove is arranged in the non-rotating component it is advantageous to move the lubrication groove in the direction of rotation of the adjacent rotating component to tend to the to obtain the above-mentioned forced funding effect. This can in two on both sides of the bearing part in question arranged lubrication grooves can be obtained when the Lubrication grooves are inclined in opposite directions and preferably by an axially or at an angle Lubrication groove are interconnected. It is preferable the inner bearing part by at least one side Support flange axially supported.

Further training features of the invention relate on the other, especially the outer or second, Bearing part limited to store ball. The latter can by the fact that the second bearing part with a a transverse plane arranged spherical section Shell surface is formed with which it is in a hollow spherical segment-shaped recess of a third Bearing part or a housing wall sits. This will in addition to at least one-sided axial support spherical slewing bearing created that z. B. by Bends of the associated shaft resulting Compensates for misalignment and thereby the bearing Protects wear and overuse.

Other developments of the invention relate to that rotary slide bearing with regard to its mountability or Improve disassembly and simple, small as well maintain reliable construction methods with a long service life.

Advantageous embodiments of the rotary slide bearing according to the invention with reference to the drawing explained. It shows:

Figure 1 shows an axial piston machine in axial section.

Figure 2 shows the Figure 1 marked with detail II according to the invention with a sliding pivot bearing in an enlarged sectional view..;

Fig. 3 shows the partial section III-III in Fig. 2;

Fig. 4 shows an inventive rotary plain bearing in perspective view a package portion, partly in section;

Fig. 5, the sliding pivot bearing according to Figure 4 in a different functional position.

Fig. 6, the sliding pivot bearing in a pre-assembly;

Fig. 7 is an outer bearing part of the rotary sliding bearing in axial section;

Fig. 8, the swivel slide bearing in a modified embodiment in axial section;

9 shows the rotary plain bearing in a further modified embodiment in axial section.

Fig. 10, the sliding pivot bearing in a further modified embodiment in axial section;

11 shows an inventive rotary plain bearing in a modified embodiment in axial sectional view.

FIG. 12 is a second and a third bearing portion of the rotary plain bearing in perspective view;

FIG. 13 is a section of the rotary sliding bearing in the front view;

Fig. 14 in Fig. 1 with marked XIV detail with an inventive sliding bearing in a modified configuration, and an enlarged sectional view.

The piston machine shown in FIG. 1, which is designed as an example and designated in its entirety by 1, has a housing 2 , in the interior 3 of which a swash plate 4 and a cylinder drum 5 are arranged side by side. In the cylinder drum 5 , piston holes 6 are arranged distributed around the circumference, which in the present exemplary embodiment of an axial piston machine extend essentially parallel to a central axis 7 of the cylinder drum 5 and are open on the face 5 a of the cylinder drum 5 facing the swash plate 4 .

In the bushing holes 6 guide bushings 8 are firmly inserted, preferably pressed.

In the guide bushes 8 , cylindrical pistons 9 are preferably mounted in an essentially axially displaceable manner, and their piston heads limit working chambers 11 in the cylinder drum 5 in the direction of the swash plate 4 . The foot ends of the pistons 9 facing the swash plate 4 are each supported by a joint 12 on the swash plate 4 , whereby sliding shoes 13 may be present, between which and the foot ends the joints 12, which are preferably designed as ball joints with a ball head and a ball recess, are arranged.

The cylindrical drum 5 lies with its face facing away from the swash plate 4 against a control disc 14 , in which at least two control openings 15 are arranged in the form of kidney-shaped through holes, which form sections of an indicated supply line 16 and a discharge line 17 , which are formed by an adjacent housing wall 18 extend on which the control disc 14 is held. The cylinder drum 5 is arranged on a drive shaft 19 which is rotatably mounted in the housing 2 and whose axis of rotation 21 extends coaxially with the central axis 7 of the cylinder drum 5 .

In the present exemplary embodiment, the housing 2 is formed from a pot-shaped housing part 2 a with a housing base 2 b and a peripheral wall 2 c and a cover or connecting part 2 d forming the housing wall 18, which bears against the free edge of the peripheral wall 2 c and thus is screwed by indicated screws 22 . To connect the further supply and discharge lines 16 , 17 , 2 d line connections 16 a, 17 a are provided on the connecting part. The drive shaft 19 , which passes through the cylinder drum 5 in a bearing bore, is rotatably supported and sealed in bearing recesses in the housing base 2 b and the cover 2 d by means of suitable bearings 25 , 25 a, whereby it axially penetrates the housing base 2 b and with a drive pin 19 a protrudes from the housing base 2 b.

In the embodiment of the piston machine 1 as a swash plate machine, the cylinder drum 5 by a rotary driving connection 26 , for. B. a toothed clutch, rotatably arranged on the drive shaft 19 , these z. B. firmly arranged on the housing base 2 or formed therein swash plate 4 in a through hole 27 . In the present exemplary embodiment, the cylinder drum 5 rotates relative to the swash plate 4 in functional operation, the pistons 9 being displaced longitudinally in the direction of the working chambers 11 and back.

In the embodiment, the rear, in the housing wall 18 or in the connecting part 2 d mounted bearing 25 a is a rotary slide bearing 25 b, which is combined with a spherically movable rotary slide bearing 25 c, so that it is able to rotatably support the drive shaft 19 and also to compensate for deficiencies in the alignment of the bearings 25 , 25 a and / or deflections of the drive shaft 19 which occur in functional operation. This prevents or reduces canting in the rotary slide bearing 25 b, which improves the sliding function, reduces the friction and heating in the rotary slide bearing 25 d and increases the service life.

The combined in the above-described spherical rotary slide bearing 25 c has an inner first bearing part 31 with an outer first sliding surface 31 a, with which it is rotatably mounted in an outer second bearing part 32 with an inner second sliding surface 32 a with sliding play. As a result, the outer second bearing part 32 surrounds the inner first bearing part 31 , the outer second bearing part 32 being formed, at least on its outer circumference, as a ring with a spherical zone-shaped outer third bearing surface 32 b, with which it is of limited spherical movement. I.e. it can be tilted on all sides with respect to the axis of rotation 21 , is mounted in a third bearing part 33 with an inner fourth bearing surface 33 a which is at least partially shaped in the manner of a spherical segment.

In the embodiment, the second bearing part 32 and the third bearing part 33 are formed as rings which, for. B. may have an equal axial width b. In the embodiment, the first bearing part 31 is formed wider than the second and the third bearing part 32 , 33 , whereby these z. B. towered on both sides.

In addition, in the exemplary embodiment, the first bearing part 31 is formed by a bearing sleeve 31 b, preferably a hollow cylindrical cross section, which is arranged on a bearing pin 19 a of the drive shaft 19 in a rotationally fixed manner, for. B. with a press fit on the journal 19 a.

The third bearing part 33 is preferably also a bearing sleeve 33 b, which sits in a rotationally fixed manner in or on the component carrying it, here on the cover or connecting part 2 d. For this purpose, a bearing bore 34 is provided for the round third bearing part 33 , preferably with a shoulder surface 34 a formed by an inner step, which delimits the third bearing part 33 axially outwards. In the embodiment, the bearing bore 34 extends inwards over the dividing surface 2 e between the connecting part 2 d and the control disk 14 into the latter, preferably also a shoulder surface 34 b is arranged here, which delimits the outer bearing part 33 inwards, thereby axially is positioned positively. In this embodiment, the bearing sleeve 33 b forms a centering pin for centering the control disk 14 .

The exemplary embodiments according to FIGS. 1 to 9 and 11 to 13 are set up for a rotary movement between the first and the second bearing part 31 , 32 and for a ball movement or tilting movement between the second and the third bearing part 32 , 33 . Around a rotational movement about the axis of rotation 21 between the second and the third bearing element 32 to prevent 33, 33 a positive fit effective rotation-blocking arrangement is arranged between the second and third bearing elements 32, 35 with a pivot link provided. The pin connection comprises one of these two bearing parts 32 , 33 protruding and in a slot 35 a of the other bearing part 32 , 33 enclosing locking pin 35 b, the slot 35 a extending along the axis of rotation 21 . In addition, the slot 35 a and the locking pin 35 b are in the radial plane Er containing the center of curvature M of the bearing part 32 , 33 in question . As a result, a rotary movement between the bearing parts 32 , 33 is blocked, but a limited all-round tilting movement is possible, which allows the above-described compensatory measures.

The locking pin 35 b can be formed by a round pin 35 c, which is seated in a bore in the one bearing part 32 , 33 , for. B. is pressed, and with its outstanding, z. B. thickened, head in the slot 35 a of the other bearing part 32 , 33 rims with movement. In the exemplary embodiment, the pin hole is arranged in the second bearing part 32 and the elongated hole 35 a is arranged in the third bearing part 33 .

The locking pin 35 b is preferably arranged in the longitudinal center plane E intersecting the control openings 15 symmetrically or in the longitudinal center plane E1 extending at right angles thereto. This is because the sum of the piston forces exerts a resulting transverse force on the drive shaft 19 which is effective in the longitudinal center plane E and which, as torque, can cause a slight bending of the drive shaft 19 which is compensated for by a tilting movement in the longitudinal center plane E. This tilting movement can be carried out by the ball-movable bearing 25 c in all transverse directions without any problems, in particular when the elongated hole 35 a extends in the longitudinal center plane E or also when it is located in the longitudinal center plane E1. In this position, a previously described tilting movement takes place about the transversely extending central axis of the locking pin 35 b.

The third bearing part 33 has on one side an axial insertion groove 36 , which is larger with respect to its transverse dimensions A, B and its cross-sectional shape than the axial cross-sectional size and shape of the second bearing part 32 , so that the latter in an angularly rotated position, for. B. in a position rotated by about 90 ° into the insertion groove 36 . The axial length of the insertion groove 36 is dimensioned so large that the second bearing part 32 can be pushed into an intermediate position according to FIG. 5, in which the centers of curvature of the third and fourth bearing surfaces 32 a, 33 a lie in the common center of curvature M and therefore cover. In this position, the second bearing part 32 can be rotated into its end position, in which its longitudinal central axis is approximately aligned with the longitudinal central axis of the third bearing part 33 . In this turned-back end position, the second bearing part 32 is axially positively positioned in the third bearing part 33 by the undercut of the fourth bearing surface 33 a in the form of a spherical segment.

In the exemplary embodiment, two insertion grooves 36 are arranged diametrically opposite one another and mirror images of one another, so that the second bearing part 32 can be inserted centrally into the third bearing part 33 . The opposite, preferably in cross-section corresponding to the diameter D of the second bearing part 32 base 36 a of the insertion grooves 36 are preferably formed tangentially to the spherical segment-shaped fourth bearing surface 33 a, so that they run out in the middle of the third bearing part 33 and into the spherical segment-shaped fourth bearing surface 33 a pass. This has the particular advantage that the introduced second bearing part 32 to the the insertion grooves a stops for the insertion movement of the second bearing member 32 is 36 axially opposite portions of the spherical segment-shaped fourth bearing surface 33 and that in the intermediate position in which the centers of curvature overlap each other and the second Bearing part 32 is rotatable. This ensures simple and user-friendly assembly. The second bearing part 32 only needs to be moved up to an insertion stop and then rotated.

In the exemplary embodiment, the width B of the at least one insertion groove 36 is approximately 1/2 to 1/3 of the diameter D of the second bearing part 32 . With this size there are in addition to the at least one insertion groove 36 sufficiently large sections of the spherical section-shaped fourth bearing surface 33 a, which ensure the positive engagement in this axial direction.

An interference fit between the circumference of the third bearing part 33 and the wall of the bearing bore 34 can be used to secure the third bearing part 33 against rotation in the housing wall 18 . In the embodiment according to FIG. 8, in which the same or comparable parts are provided with the same reference numerals, an interlocking rotary locking device 37 in the form of a pin connection is also provided for securing the third bearing part 33 against rotation in the housing wall 18 or in the connecting part 2 d. Preferably, this serves b of the locking pin 35, the bordered by the third bearing portion 33 and a bordering in a the long hole 35 substantially corresponding elongated hole 37 a in the housing wall 18th In this embodiment, not only the second bearing part 32 but also the third bearing part 33 is positively positioned on the housing wall 18 against rotation in the circumferential direction.

The assembly of the second bearing part 32 and the insertion of the locking pin 35 b into the slot 35 a takes place in that the second bearing part 32 is inserted in a position in which it is rotated with the locking pin 35 b with respect to the slot 35 a ( Fig in that the locking pin 35 is. 6) b in the insertion groove 36 inserted. If the locking pin 35 b is in the region of the elongated hole 35 a, the second bearing part 32 is turned back, the locking pin 35 b being immersed in the elongated hole 35 a. This is easily possible due to the spherical section-like shape of the second bearing part 32 .

Also in the embodiment of Fig. 8, it is possible with an appropriate dimensioning, the elongated locking pin 35 b as in the long holes 35 a, introduce 37 a, is introduced that the second bearing part 33 is rotated and is then rotated back, as according to Embodiment has been Fig. 2 to 6 already described. However, it is also possible that the slot 37 a runs out to the side from which the third bearing part 33 can be inserted into the bearing bore 34 . In this embodiment, the third bearing part 33 with the second bearing part 32 mounted therein can be inserted into the bearing bore 34 , the locking pin 35 b being simultaneously inserted into the elongated hole 37 a. In the exemplary embodiment according to FIG. 8, this is possible from the inside, since the elongated hole 37 a runs out to the dividing surface 2 e between the housing wall 18 and the control disk 14 and this spherically movable rotary slide bearing 25 c before the control disk is attached to the housing wall 18 or before Cultivation of the housing wall 18 can be mounted on the control disk 14 .

In the embodiment according to FIG. 9, in which the same or comparable parts are provided with the same reference numerals, a different embodiment of the anti-rotation device 37 is provided, wherein the anti-rotation device 35 can be designed according to FIG. 8. According to FIG. 9, the anti-rotation device 37 is also formed by a pin connection, but this is not arranged transversely but axially parallel with respect to the axis of rotation 21 and is formed by a locking pin 37 c, which is arranged in the region of the step surface and in mutually opposite holes in the housing wall 18 and borders in the third bearing part 33 .

The embodiment of FIG. 10, in which the same or comparable parts are also provided with the same reference numerals, makes it clear that a separate third bearing part 33 is not required if the inner fourth bearing surface 33 a and the at least one insertion groove 36 directly on the housing wall 18 or the connecting part 2 d are formed. In this exemplary embodiment too, locking devices in the sense of FIGS. 8 or 9 can be provided, wherein the elongated hole 35 a can be arranged in the housing wall 18 (not shown).

In the present reciprocating engine or axial piston machine 1 is located in the interior 3 of hydraulic liquid such. B. hydraulic oil, which can be used in operation to lubricate the sliding surfaces 31 a, 32 a and preferably also the bearing surfaces 32 b, 33 a. A water-containing lubricant which contains approximately 50% water and approximately 50% glycol and is known in specialist trade under the name HFC is particularly suitable as the lubricant.

In order to ensure the accessibility of the lubricant located in the interior 3, in particular to the rotary slide bearing 25 b, it is advantageous to provide an axial passage 14 a between the control disk 14 and the drive shaft 19 , which ensures the access of the lubricant at least to the rotary slide bearing 25 b. In the exemplary embodiment, the control disk 14 has a through hole which surrounds the drive shaft 19 with a ring spacing. The diameter D1 of the through hole is preferably larger than the outer diameter of the first bearing part 31 or the bearing sleeve 31 b, so that an annular access to the sliding surfaces 31 a, 33 a and preferably also to the bearing surfaces 32 b, 33 a is ensured.

To further improve the lubrication, it is advantageous to provide in at least one of the sliding surfaces 33 a, 32 a, here in the inner second sliding surface 32 a, one or more lubricating grooves 38 which are distributed over the circumference and can extend axially or at an angle or helically , as shown in FIGS. 2 to 7. In the case of an oblique or helical arrangement of the at least one lubrication groove 38 , a load-bearing region B1 results on each axial side of the second bearing part 32 , which is delimited by the associated edge of the lubrication groove 38 and an axially extending sliding surface line 39 .

In the above-described exemplary embodiments, the rotary slide bearing 25 c is a so-called floating bearing with respect to the drive shaft 19 , ie there is no mutual axial support between the drive shaft 19 or the first bearing part 31 and the second bearing part 32 arranged thereon. In contrast, this axial support is present between the third bearing part 33 and the housing 2 or the housing wall 18 receiving the rotary sliding bearing 25 b. However, there are also applications in which an axial support between the first and the second bearing part 31 , 32 is desired in at least one axial direction. This can be achieved in that the second bearing part 32 is bounded on one or both sides by a shoulder or sliding surface which is arranged on the drive shaft 19 or an attachment part thereof. Such a rotary slide bearing, which is designed as a fixed bearing in at least one axial direction, can be formed with two bearing parts 31 , 32 as a rotary slide bearing 25 b or with the second and third bearing parts 32 , 33 as a tiltable rotary slide bearing 25 c and thus in one or in both axial directions Absorb axial forces.

In the embodiment according to FIG. 11, in which the same or comparable parts are provided with the same reference numerals, the rotary slide bearing 25 c is arranged as a fixed bearing which is effective in both axial directions in the region of the housing 2 , here in the housing base 2 b, being in the connecting part 2 d arranged bearing 25 a or preferably the bearing 25 arranged in the housing base 2 b can form, as shown in FIG. 11. The second bearing part 32 is delimited on both ends by a support flange 42 a, 42 b with play, which is axially fixed to the drive shaft 19 or to the first bearing part 31 . In the embodiment, a support flange, here the outer support flange 42 a is integrally connected to the first bearing part 31 , these parts forming an angular ring body, and the inner support flange 42 b has a coaxial hole 43 , with the edge of the hole of which he moves with little movement on the Drive shaft 19 sits. On the side facing away from the rotary slide bearing 25 c, the support flange 42 b can be axially supported by a drive shaft shoulder 44 , which in the exemplary embodiment is formed by a spring ring which is seated in an annular groove in the drive shaft 19 . The first bearing part 31 preferably extends to the surface of the second support flange 42 b facing it and it is axially supported in the other axial direction, here outwards, by a drive shaft shoulder 45 , which can protrude in one piece from the drive shaft 19 as a flange ring.

For lubrication, one or more lubrication grooves 46 are arranged in the shoulder or sliding surfaces 42 c of the support flanges 42 a, 42 b (not shown) or in the end surfaces 32 c of the second bearing part 32 , and are distributed on the circumference and extend from the inside to the outside a, 46 b are provided, which are connected radially on the inside with a lubricant supply line and radially on the outside with a lubricant discharge line and are thus part of a lubricant circuit 47 through which a lubricant flows during operation of the piston machine, for. B. of hydraulic oil. In order to maintain the flow in the lubricant circuit 47 , no special lubricant pump is required. The lubricant in operation in the lubrication grooves 46 a, 46 b generates the flow in the circuit 47 automatically due to the centrifugal force acting on the lubricant. The lubricant circuit 47 can, for. B. be connected to the interior 3 of the housing 2 .

An additional conveying effect on the lubricant can be achieved if the lubrication grooves 46 a, 46 b are inclined, in particular the lubrication grooves 46 a on one side and the lubrication grooves 46 b on the other side are inclined in opposite directions. It can be located in the rotating bearing part, here in the support flanges 42 a, 42 b, lubricating grooves 46 a (not shown) opposite to the direction of rotation of the rotating bearing part or the lubricating grooves located in the non-rotating bearing part, here in the second bearing part 31 46 a, 46 b are inclined in the direction of rotation. The slope can also be spiral. In these configurations, a forced delivery effect on the lubricant is generated by the contact between the sliding surfaces, here the support flanges 42 a, 42 b, and the lubricant columns located in the lubrication grooves 46 a, 46 b. In the embodiment in which the lubrication grooves 46 a, 46 b are arranged in the non-rotating second bearing part 32 , the forced conveying effect is generated by the contact which the sliding surfaces 42 c of the rotating first bearing part 31 formed by the support flanges 42 a, 42 b generates.

In the exemplary embodiment, on both sides of the second bearing part 32 and associated lubrication grooves 46 a, 46 b are connected to the at least one lubrication groove 38 , which can be located in the outer surface of the first bearing part 31 or in the inner surface of the second bearing part 32 and thereby can extend axially, as z. B. Fig. 4 and 5, or may extend obliquely, as shown in Fig. 7, for example. With an oblique course of the lubrication groove 38 , the forced delivery effect is also generated in the area of the lubrication groove 38 . The conveying effect is generated by the contact which the sliding surface adjacent to the lubricant in the at least one lubrication groove 38 exerts on the lubricant. Here, the interconnected by the straight oil groove 38 oil grooves 46 a, 46 b or the interconnected by an inclined oil groove 38 lubricating Below 46 a, 46 b and the inclined oil groove 38 oriented so that the conveying action is efficacious in successive directions, and there is a continuous conveying effect in the lubrication groove sections 46 b, 38 , 46 a. In operation, the lubricant then enters the radially outer end of the lubrication groove or grooves on one side and exits the radially outer end of the lubrication groove or grooves on the other side. The axial course of the conveying action or the conveying direction outwards or inwards is dependent on the direction of rotation of the drive shaft 19 or of the first bearing part 31 .

In the exemplary embodiment, the lubricant circuit 47 is formed in that the inside lubricant grooves 46 b are open radially outside to the interior 3 . The outside lubrication grooves 46 a are also open radially on the outside and they can also be connected to the interior 3 by a lubricant channel, not shown.

Fig. 11 shows an embodiment in which in addition to the lubricant circuit 47, a pivot bearing lubrication is included for a known pivotable swash plate 4. In this embodiment the lubricant grooves 46 terminate a radially outward into a preferably annular gap or lubricant channel portion 47 a, of which b in the housing base 2 is a further lubricant channel leading b 47 z. B. extends angularly to the slide bearing surface 48 of a pivot bearing 49 for the swash plate 4 pivotably mounted in this embodiment and thereby penetrates a bearing shell 51 of the pivot bearing 49 . The pivot bearing 49 arranged on the other side of the piston machine 1 with respect to the axis of rotation 7 of the drive shaft 19 can be connected in the same way to the lubricant circuit 47 , which is not shown for reasons of simplification.

In the exemplary embodiment, the flow directions of the circuit flow in the region of the rotary slide bearing 25 c, starting from the openings of the lubrication channels 46 b, are initially directed radially inward, then axially outward and then radially outward, see S1, S2, S3.

Fig. 13 shows the oppositely inclined lubrication grooves 46 a, 46 b on both sides of the second bearing part 32nd

In the embodiment of Fig. 12 an axially acting rotary fuse 37 is formed in that the annular body of the third bearing member 33, one or more z. B. axially projecting two opposing segments 37 d, the positioning recesses arranged directly or indirectly on the housing 2 or housing base 2 b, into which they border or one or more positioning pins which extend into the at least one recess 37 e present between two segments frame, interact positively for the purpose of securing against rotation.

In the embodiment, the rotary slide bearing 25 c sits with its third bearing part 33 in a bearing bore 61 , which has a stop shoulder 62 on the inside for the third bearing part 33 and is widened step-wise towards the outside, with a locking ring 64 with an annular seal 65 for the in the larger bore step 63 Drive shaft 19 is used and axially secured by a retaining ring 66 .

In the embodiment according to FIG. 14, in which the same or comparable parts are also provided with the same reference numerals, an axial support of the second bearing part 32 according to FIG. 11 is realized in a rotary slide bearing 25 b, which is not ball-movable, and its outer second bearing part 32 is cylindrical and in an adapted bearing bore 61 z. B. is used in the housing base 2 b. Otherwise - including the arrangement and configuration of the support flanges 42 a, 42 b and the lubrication grooves 46 a, 46 b - the configuration according to FIG. 14 corresponds to that according to FIG. 11, to which reference is made in full and therefore no further description is given can.

Claims (17)

1. rotary slide bearing ( 25 c), in particular for a drive shaft ( 19 ) of a piston machine, preferably an axial piston machine ( 1 ), which has an inner first bearing part ( 31 ) with a lateral surface ( 31 a) and an outer second bearing part ( 32 ) with a Has inner surface ( 32 a), the outer bearing part ( 32 ) surrounding the inner bearing part ( 31 ),
wherein in the lateral surface ( 31 a) of the inner first bearing part ( 31 ) and / or in the inner lateral surface ( 32 a) of the outer second bearing part ( 32 ) at least one axially continuous first lubrication groove ( 38 ) is provided,
One of the two bearing parts ( 31 ) on one or both sides is assigned a support shoulder ( 42 a, 42 b) with a sliding surface ( 42 c) on which the bearing part ( 32 ) with its side surface ( 32 c) facing it axially is supported
wherein at least one approximately radial second lubrication groove ( 46 a, 46 b) is arranged in each case in the sliding surface ( 42 c) or in the side surface ( 32 c) supported thereon, and wherein the lubrication grooves ( 46 a, 46 b, 38 ) in mutually facing area are connected. 2. rotary slide bearing according to claim 1, characterized in that on at least one side of the bearing part ( 31 ) or ( 32 ) the at least one lubrication groove ( 46 a, 46 b) is inclined in a circumferential direction. 3. rotary slide bearing according to claim 2, characterized in that the lubrication grooves ( 46 a, 46 b) are arranged on both sides, which are inclined to each other in opposite directions. 4. rotary slide bearing according to one of the preceding claims, characterized in that the lubricating groove ( 38 ) extends obliquely. 5. rotary slide bearing according to one of the preceding claims, characterized in that the lubrication grooves ( 46 a, 46 b, 38 ) are part of a flow circuit ( 47 ) which is preferably connected to the interior ( 3 ) of the piston machine. 6. rotary sliding bearing according to one of the preceding claims, characterized in that the or one of the two support shoulders ( 42 a) is integrally connected to the one bearing part, in particular the first bearing part ( 31 ). 7. rotary sliding bearing according to one of the preceding claims, characterized in that a support shoulder ( 42 b) is formed by a separate annular disc, which is preferably seated on the drive shaft ( 19 ). 8. rotary slide bearing according to one of the preceding claims, characterized in
that the outer bearing part ( 32 ) is formed on its outer circumference with a spherical section-shaped third bearing surface ( 32 b) with which it is limitedly movable in a third bearing part ( 33 ) with a spherical section-shaped inner fourth bearing surface ( 33 a), which is the third Surrounding storage area ( 32 d),
and that at least one insertion groove ( 36 ) is arranged on one side of the third bearing part ( 33 ), in which the second bearing part ( 32 ) can be inserted into the third bearing part ( 33 ) in an angularly rotated position up to a position in which the centers of curvature (M) of the third and fourth bearing surfaces ( 32 b, 33 a) essentially cover one another. 9. rotary slide bearing according to claim 8, characterized in that two insertion grooves ( 36 ) are arranged opposite one another. 10. rotary slide bearing according to claim 9, characterized in that the base surfaces ( 36 a) of the insertion grooves ( 36 ) tangentially into the spherical segment-shaped fourth bearing surface ( 33 a). 11. rotary slide bearing according to one of claims 8 to 10, characterized in that the width (B) of the insertion groove ( 36 ) is approximately 1/3 to 1/2 of the diameter (D) of the second bearing part ( 32 ) and the width (b ) of the second bearing part ( 32 ) is smaller than the width (B) of the insertion groove ( 36 ), at least taking into account a play of movement. 12. rotary slide bearing according to one of claims 8 to 11, characterized in that between the second and the third bearing part ( 32 , 33 ) a rotary locking device ( 35 ) is arranged. 13. A sliding pivot bearing according to one of claims 8 to 12, characterized in that the rotary locking device (35) is formed by a journal connection between the second and third bearing elements (32, 33) and at the one bearing part (32) fixed locking pin (35 b) with axial movement play in a recess formed preferably by an axial slot ( 35 a) in the other bearing part ( 33 ). 14. rotary slide bearing according to one of claims 8 to 13, characterized in that the third bearing part ( 33 ) is a sleeve-shaped bearing part which is seated in a bearing bore ( 34 ) of an additional bearing part. 15. rotary slide bearing according to claim 14, characterized in that the additional bearing part is formed by a connecting part ( 2 d) of a piston machine, in particular an axial piston machine ( 1 ). 16. rotary slide bearing according to claim 15, characterized in that the sleeve-shaped bearing part is limited on the inside by a control disc ( 14 ) which is arranged on the inside of the connecting part ( 2 d). 17. rotary slide bearing according to claim 15 or 16, characterized in that on the inside of the connecting part ( 2 d) a control disc ( 14 ) is arranged, wherein in the control disc ( 14 ), or between the control disc ( 14 ) and one of the first bearing part ( 31 ) supporting drive shaft ( 19 ) an axial passage ( 14 a) is provided for a lubricant.