DE102021124857A1 - Tilting pad bearings, in particular radial tilting pad plain bearings - Google Patents

Abstract

The invention relates to a tilting pad bearing for supporting a shaft or axle, comprising a bearing housing with a bearing bore aligned along a bearing axis and at least two tilting pads which can be moved relative to the bearing housing and are spaced apart from the bearing axis in the circumferential direction around the latter, with each individual tilting pad having a radially inner one Bearing surface and a radially outer surface for support on a bearing surface on the bearing housing and has segment side surfaces connecting these to one another and pointing in the circumferential direction to the adjacent tilting segment, and the transition between bearing surface and individual segment side surface describes a first and a second segment edge on the tilting segment. The invention is characterized in that; that at least one of the segment side surfaces of an individual tilting segment, which faces in the circumferential direction in the installed position, has at least one partial area, viewed in the direction of extension from the bearing surface to the radial outer surface, which is set back compared to a theoretical plane that can be described in the radial direction by the respective segment edge through the bearing axis and a perpendicular to it .

Description

The invention relates to a tilting pad bearing, in particular a radial tilting pad plain bearing, in detail with the features of the preamble of claim 1.

Such tilting pad bearings are known in various forms from the prior art. These comprise at least two tilting segments which are spaced apart from one another in the circumferential direction and each have a bearing surface which functions as a sliding surface. These tilting pads are mostly lubricated individually with a medium, usually oil, which forms a lubricating film. The lubricating film is located in a lubricating gap between the bearing surface of each of the tilting pads and the shaft to be supported, with the oil being conveyed through this lubricating gap due to the rotation of the shaft. Due to the load, the oil heats up and leaves the gap at a higher temperature than when it entered the lubricating gap. Tilting pad bearings can be provided for both directions of rotation or for a specific direction of rotation of the shaft. Each of the tilting segments has a first segment edge provided at the entry into the bearing surface and a second segment edge downstream of this segment edge in the direction of rotation of the shaft on the bearing surface. The first segment edge is that which is first traversed by a point on the rotating shaft (leading edge), while the second trailing or trailing segment edge is that which is last traversed by the point on the shaft (trailing edge).

In order to ensure high performance of such bearings, in particular to be able to use them for high rotational speeds and high mechanical loads, it is necessary to dissipate the heat generated during operation in the lubricating film in a targeted and efficient manner. Various approaches are known for this, which are characterized, among other things, by an increased supply of cooler oil and targeted removal of heated oil and/or special guidance of cooling medium on the tilting segment.

The research project "FVA 677 II, IGF 19926 N" deals with influencing the flow in the lubricant supply area of radial tilting pad bearings to reduce maximum bearing temperatures and increase the power density. The oil supply is designed in such a way that it flows directly onto the tilting pad and utilizes the niche flow induced by the shaft rotation.

CN102518670A discloses a tilting pad bearing with tilting pads having oil passages on the pad side faces. Furthermore, the segment lower edges are recessed or provided with a plurality of grooves in order to improve cooling by the lubricant. However, the grooves are also susceptible to contamination due to contamination in the oil and can become clogged, which means that the advantage of guiding cooling oil is no longer given. Furthermore, an additional manufacturing step for producing the grooves is required, which is associated with additional costs.

Further versions provide for the use of additional nozzles for introducing cooling oil.

DE19514830 C2 describes an arrangement of oil nozzles in tilting pad bearings, in which an opening of the nozzles is aimed directly at the pad trailing edge. JP5026230 A2 describes an arrangement of the nozzles tangential to the surface of the shaft. The disadvantage of such nozzle arrangements is that this type of oil supply does not utilize the niche flow downstream of the outlet edge and induced between the adjacent tilting segments by the shaft rotation, but rather impedes it, with the result that heat transfer can only take place to a limited extent. In addition, large gaps between the tilting pads are required for such an arrangement in order to ensure accessibility for the oil nozzles. The large gaps in the segments mean that the angles of enclosure of the segments themselves are smaller.

JP58180815 A2 describes an embodiment of an oil nozzle for supplying cooling oil with openings in two directions, namely in the direction and against the direction of shaft rotation. The warm oil is to be removed from the shaft by the oil escaping from the nozzle.

WO19163162A1 describes an embodiment utilizing the niche flow in the segment pocket between two adjacent tilting segments through the possibility of adjusting the nozzle opening relative to the tilting segment in the circumferential direction.

In addition to the designs with additional nozzles and their design, measures to increase the performance through measures directly on the tilting segment are also known.

So revealed JP2019056429A a tilting pad design in which the tilting pad has recesses in the axial direction on the radial outer surface. The oil supply is arranged in this recess. The disadvantage of this patent is that the recess weakens the tilting pad itself. Due to the weakening, a higher deformation of the segment is to be expected, which has negative effects gene on the temperature education. Furthermore, an additional manufacturing step is required to produce this recess, which causes additional costs.

The following publications disclose a wide variety of different embodiments of tilting pads that have internal channels through which oil flows in order to ensure better cooling: US9874247 BB, JP2016191402 A2 , JP6325915 B2 , WO14208196 A1 , JP6304471 B2 , US9739310 BB, US8834032 BB, JP4930290 B2 , KR100799546 B1 , JP2009030704 A2 , US9611886 BB, US9759257 bb The main disadvantage is that internal ducts require additional/complicated/not yet suitable manufacturing processes for economical series production, which causes additional costs. In addition, the tilting segment is weakened by the internal channels, which results in higher segment deformation under load.

The following publications deal with a wide variety of designs for oil supply to the tilting pad/tilting pad edges in order to ensure better cooling: DE112017001058 T5 , JP2017141882A2 , JP2017026089 A2 , KR100817220 B1 , JP2004197890 A2 , EP2762735 A1 These different feeds of the oil to the segment edges also do not take into account the niche flow induced by the shaft rotation and thus impede it.

Different embodiments of the surfaces of tilting segment backs and edges, in order to ensure better cooling as a result of larger surfaces, are already known from the following publications: US2019024707 AA, EP2971821 B1 , CN202867564 U , JP9032848 A2 , WO19142383 A1 Their disadvantage is the susceptibility to contamination and the additional manufacturing effort required to produce such surfaces.

Another way to improve heat dissipation is to separate hot and cold oil or to separate the hot oil from the shaft using strips/lips to ensure better cooling: EP3067577 A1 , US9618048 BB, JP6101135 B2 , CN102966830A , EP2588767 B1 , US5738447A , US2019277338A , CN205780314 U , CN108591245 A. The disadvantage is that the thin thermal boundary layer containing the warm oil often cannot be separated in a process-reliable manner.

The invention was therefore based on the object of further developing a tilting pad bearing, in particular a radial tilting pad plain bearing, in such a way that it can be used for higher loads and/or rotational speeds with the same size, with the aforementioned disadvantages being avoided. The solution according to the invention should be distinguished by a low level of design and manufacturing complexity and should therefore be able to be implemented as cost-effectively as possible.

The solution according to the invention is characterized by the features of claim 1. Advantageous configurations are given in the dependent claims.

A tilting pad bearing for supporting a shaft or axle, comprising a bearing housing with a bearing bore aligned along a bearing axis and at least two tilting pads which are movable relative to the bearing housing and spaced apart from the bearing axis in the circumferential direction around the latter and are spaced apart from one another, with the individual tilting pad each having a radially inner bearing surface and a radially outer surface for support on a bearing surface on the bearing housing and has segment side surfaces connecting these to one another and pointing in the circumferential direction to the adjacent tilting segment and the transition between bearing surface and individual segment side surface describes a first and a second segment edge on the tilting segment is characterized according to the invention in that at least one of the Installation position in the circumferential direction pointing segment side surfaces of a single tilting segment viewed in the direction of extension from the bearing surface to the radial outer surface has at least a partial area t, which is set back in relation to a theoretical plane that can be described by the respective segment edge in the radial direction through the bearing axis and a perpendicular to this plane.

The solution according to the invention is based on the consideration that the temperature profile of the lubricating oil on the bearing surface is highest in the direction of rotation of the shaft to be supported in the area of the outlet from the bearing surface, the so-called trailing edge, and thus also the heat input into the tilting segment in this area. However, the temperature within the tilting segment decreases with increasing distance from this area, which means that direct cooling of these areas does not have the desired effect on the areas of the maximum temperature. In order to bring the cooling oil volume flow as close as possible to this area, a targeted but easy to implement geometry change on the tilting segment is therefore proposed, without weakening the tilting segment or keeping the weakening to a minimum. For this purpose, only the material of the Tilting segment, which is not in the power flow or only on the edge of the power flow, removed. While the segment side surfaces pointing in the circumferential direction at the segment edges, in particular the inlet and outlet edges, depending on the direction of rotation of the shaft to be mounted, usually run radially or almost radially in the prior art, this design is now deviated from and at least one individual segment side surface has at least a sub-area region that is set back in relation to the radial alignment in the segment direction. This reduces the material thickness in the area of the maximum temperature. As a result, the cooling oil volume flow to be supplied can be brought as close as possible to the area of the maximum temperature on the tilting segment directly when it enters the segment pockets between two adjacent tilting segments. This solution - cooling the area of the maximum temperature on the tilting pad - also indirectly reduces the thermal load on the lubricating oil used to operate the tilting pad bearing.

The advantage of such an embodiment is that it generates no/only a minimal amount of additional manufacturing effort, in that only the contour of the entire side surface has to be manufactured or processed. Since this is free of grooves, undercuts, etc., this geometry is robust against dirt. Furthermore, the formation of the induced niche flow is not impeded. An advantageous flow resistance-reduced design even promotes the formation of the niche flow induced by the shaft rotation.

With regard to the specific geometry of the segment side surfaces, there are a number of possibilities for implementing the set-back according to the invention. The selected geometry of the segment side faces can be characterized in a view on a plane that can be described by two perpendiculars to the bearing axis running perpendicular to one another, by a profile which, in an advantageous embodiment, is viewed in the longitudinal direction of the tilting segment, which in the installed position coincides with the direction of the bearing axis, is constant is held. I.e. the surface contour is not subject to any change in this direction. The production costs can be kept low as a result.

In an advantageous first embodiment, the at least one segment side surface of an individual tilting segment can be written on at least in a partial area of its extension, preferably completely viewed between the bearing surface and the outer surface, by a flat surface which is at an angle in the range of 20° to 45° to the theoretical one through the bearing axis and a perpendicular to this plane which can be described in the radial direction by the respective segment edge and is referred to as the segment edge radial plane. The offset in the segment, viewed in the direction of the radial outer surface, can be varied via the size of the angle between the segment edge plane and the flat surface. In an advantageous embodiment of the first embodiment, the segment side surfaces of an individual tilting segment pointing away from one another are aligned at least partially, preferably completely, parallel to one another. In particular, the completely parallel design is characterized by minimal manufacturing effort and allows a sufficient set-back for guiding the oil to be cooled.

In order to keep dead areas for the induced oil vortex from warm oil as small as possible or to avoid them entirely, even when oil to be cooled is fed into the segment pockets between the adjacent tilting segments when designed with parallel segment side surfaces, an advantageous second embodiment provides for a single segment side surface of a single segment Viewed tilting segment at least in a portion of their extension between the bearing surface and the outer surface, preferably completely to be described by a concave curved surface. It is particularly advantageous if the curvature of the concavely curved surface is at least partially in the form of an arc of a circle, cylindrical, elliptical or is characterized by at least one or a sequence of radii. With this solution, the maximum material removal on the segment, in particular the segment side, does not take place in the area of the transition to the radial outer surface but within the extent of the segment side surface and thus much closer to the area of the maximum temperature.

The individual tilting segment can be embodied symmetrically or else asymmetrically with respect to a plane which is characterized by the bearing axis and a perpendicular through the center of the extent of the bearing surface in the circumferential direction. The symmetrical configuration offers the advantage that the installation can take place independent of the direction, in particular also independently of the running direction of the shaft to be supported, while with an asymmetrical configuration, the requirements of the application can be addressed in a targeted manner.

A tilting pad bearing has at least two, preferably a plurality of tilting pads. Depending on the arrangement in the tilting pad bearing and the installation of the tilting pad bearing, these are used as a load segment or non-load segment. In order to make the bearing as simple as possible and not to have to make any special alignment of the bearing during installation, preferably all are tilting Segments are designed identically or at least the segment side surfaces of a plurality, preferably all individual tilting segments, pointing in the same direction, are designed identically.

In a particularly advantageous embodiment, the two side surfaces of an individual tilting segment that face away from one another and point in the circumferential direction in the installed position have at least one partial region, viewed in the direction of extension from the bearing surface to the radial outer surface, which, compared to a theoretical through the bearing axis and a perpendicular to this in the radial direction the respective segment edge writable level is set back. The bearing has a simple design and can therefore be installed in any direction.

For designs of bearings which are mainly to be used in only one direction of rotation of the shaft to be supported, the other of the two segment side surfaces of an individual tilting segment, viewed in the direction of extension from the bearing surface to the radial outer surface, lies in a direction through the bearing axis and a perpendicular to it radial direction writable plane. I.e. only one segment side face has the setback.

If one of the segment side surfaces, preferably the segment sliding surface of the trailing edge, is set back, but the respectively opposite segment side surface, in the preferred embodiment that on the leading edge, is not, there are also advantages in terms of production. The tilting segment is to be fixed using clamping jaws. If both the segment side faces are set back at the exit and entry edge (both edges are parallel), the position of the segment in the x-direction is not defined. For this purpose, the clamping jaws must have an additional stop in the area of the back surface and in the area of the running surface. However, the stop in the area of the running surface impedes accessibility for processing the running surface. If one of the segment side surfaces is set back, a clear positioning in the x-direction is possible during processing with unrestricted access to the running surface at the same time.

In a preferred embodiment with the segment side surface set back at the trailing edge, the oil can be guided closer to the point of the highest temperatures, so that greater heat dissipation is still guaranteed, since the maximum temperatures occur at the trailing edge during operation.

For specific application requirements, the individual tilting segments can be designed differently from one another in a further development with regard to the segment side surfaces. In particular, a different configuration of the tilting segments functioning as load segments in the installed position compared to the tilting segments functioning as non-load segments is possible. For example, it is conceivable that only the loaded tilting segments have the resets and the unloaded segments form the radial surface, i.e. are formed according to the standard design. This means that standard bearings that have been in use up to now can be modified by replacing (e.g. retrofitting) by only replacing the loaded segments and not all of the elements. This reduces costs compared to a complete replacement.

The solution according to the invention is particularly suitable for tilting pad bearings in which the individual tilting pad is supported with the radial outer surface directly on the inner circumference of the bearing housing, with the radial outer surface of the individual tilting pad being able to be described by a radius which is smaller than the inner radius of the bearing housing. The guidance of the tilting segment is thus firmly specified by the bearing housing and free of additional measures, such as additional pressure blocks, etc. between the tilting segment and the bearing housing. The overall structure of the bearing is simple and can also be produced inexpensively due to the low production requirements.

In a further development it is provided that a device for supplying cooling oil is arranged in a segment pocket, which is delimited by the mutually facing segment side faces of two mutually adjacent tilting segments, or opens into this through the bearing housing. The device for supplying cooling oil has the advantage that it is designed as a "slit nozzle", so that the supplied oil reaches the segment pocket over the entire bearing width/a large part of the bearing width and not just at certain points, as would be the case when using individual oil nozzles. Cooling oil supplied across the width of the bearing promotes a more homogeneous development of the flow in the segment pocket.

Furthermore, the cooling oil can be guided to the segment outlet edge in a targeted manner by the oil supply device, which supports the formation of the flow vortex in the segment gap. is designed as a "slit nozzle" so that the supplied oil reaches the segment pocket over the entire bearing width/a large part of the bearing width and not just at certain points, as would be the case when using individual oil nozzles. Cooling oil supplied across the width of the bearing promotes a more homogeneous development of the flow in the segment pocket.

Furthermore, the cooling oil can be guided to the segment outlet edge in a targeted manner by the oil supply device, which supports the formation of the flow vortex in the segment gap.

• 1a ein Kippsegmentlager mit Kippsegmenten gemäß einer ersten Ausführung in der Ansicht auf die Lagerbohrung;
• 1b einen Ausschnitt aus 1a;
• 1c ein Kippsegment gemäß 1a, 1b in perspektivischer Darstellung;
• 2 ein Kippsegment gemäß einer zweiten Ausführung mit konkav gekrümmter Fläche in perspektivischer Darstellung
• 3 ein Kippsegment gemäß einer kombinierten Ausführung mit konkav gekrümmter und ebener Fläche in perspektivischer Darstellung
• 4a und 4b einen Ausschnitt aus einem Kippsegmentlager mit Kippsegmenten gemäß 3;
• 5 ein Kippsegment mit unterschiedlich ausgebildeten Segmentseitenflächen:
• 6 ein Kippsegmentlager mit Kippsegmenten unterschiedlicher Ausführung.

The invention is explained below with reference to figures. The figures show in detail:

• 1a a tilting pad bearing with tilting pads according to a first embodiment in the view of the bearing bore;
• 1b a snippet 1a ;
• 1c a tilting segment according to 1a , 1b in perspective view;
• 2 a tilting segment according to a second embodiment with a concave curved surface in a perspective view
• 3 a tilting segment according to a combined embodiment with a concavely curved and flat surface in a perspective view
• 4a and 4b according to a section of a tilting pad bearing with tilting pads 3 ;
• 5 a tilting segment with differently designed segment side faces:
• 6 a tilting pad bearing with tilting pads of different designs.

The 1a illustrates in a simplified, schematic representation the basic structure and the basic function of a tilting pad bearing 1 designed according to the invention for storing or supporting shafts W, comprising a bearing housing 2 with a bearing bore 4 aligned along a bearing axis LA and at least two movable relative to the bearing housing 2 and spaced apart in the circumferential direction Tilting segments 3 arranged around the bearing axis LA, here by way of example 3, 3.2 to 3.5, according to a first embodiment in a front view. The 1 b shows a section 1a on the tilting pad 3. To clarify the individual directions, a coordinate system is applied to the tilting pad bearing 1. The X axis describes the axial or longitudinal direction present in the installed position in the tilting pad bearing 1 and corresponds to the direction of the bearing axis LA. The Y-direction and Z-direction respectively describe the directions perpendicular to the X-axis and the directions perpendicular to each other. In the installed position, the Z-direction can be regarded as the height direction, while the Y-direction corresponds to the direction transverse to the longitudinal direction. The directional information and the explanations for the tilting pad bearing 1 in general, except for the design of the individual tilting pad 3 itself, also apply to the other figures.

The bearing housing 2 can be formed, for example, by a cylindrical sleeve, bushing or another base body. This can be designed in one piece or in several pieces. This preferably consists of at least two half-shells. Also conceivable is an embodiment consisting of several partial shells, which are arranged adjacent to one another in the circumferential direction about the bearing axis LA and can be connected to one another in a non-positive and/or non-positive manner.

The tilting pad bearing 1 also comprises at least 2, preferably several, tilting pads 3 according to the invention, here by way of example 3, 3.2 to 3.5, arranged movably relative to the bearing housing 2 and spaced apart from the bearing axis LA in the circumferential direction around this mutually adjacent tilting pad. The tilting segments 3, 3.2 to 3.5 are used to store and support a shaft, not shown here, about its longitudinal axis. The individual tilting segments 3, 3.2 to 3.5 in the installed position in the radial direction, starting from the bearing axis coinciding with the longitudinal axis LA, each comprise a radially inner bearing surface 5 and a radial outer surface 6, with which the individual tilting segments 3, 3.2 to 3.5 at least indirectly on a connection component, in particular a bearing surface 7 on the bearing housing 2. For reasons of clarity and simplification, the description and labeling on the segments is given as an example for the tilting segment 3. Here, the support takes place directly with the radial outer surface 6 on the inner circumference 8 of the bearing housing 2, which forms the supporting surface 7. The support does not take place over the entire surface but over a line or part of the surface . For this purpose, the radial outer surface 6 of the individual tilting pad 3 can be described by a radius r3-A, which is smaller than the inner radius r2-1 of the bearing housing 2.

The individual tilting segment 3 also has a segment side surface 9.1, 9.2 connecting the bearing surface 5 and the radial outer surface 6 and pointing in the circumferential direction, with the transition between bearing surface 5 and individual segment side surface 9.1 or bearing surface 5 and segment side surface 9.2 each having a first and a second Segment edge 10.1, 10.2 on tilting segment 3 describes. The segment edges 9.1 and 9.2 delimit the bearing surface 5 in the circumferential direction. In the installation position, these each correspond to an inlet edge and an outlet edge. The terms inlet edge and outlet edge refer to the arrangement of the tilting segment 3 relative to a shaft and its direction of rotation. The segment edge reached first in the direction of rotation of the shaft, here 9.1, is referred to as the inlet edge, and the segment edge 9.2 lying behind the inlet edge in the direction of rotation as the outlet edge.

According to the invention, at least one of the segment side surfaces 9.1 and/or 9.2 of an individual tilting segment 3, which faces in the circumferential direction in the installed position, has at least one partial region 11, viewed in the direction of extension from the bearing surface 5 to the radial outer surface 6, which is opposite to a theoretical through the bearing axis LA and a perpendicular to this set back in the radial direction through the respective segment edge 10.1, 10.2 writable plane, which is also referred to as radial plane ER-10.1, ER-10.2. The area characterized by the offset is denoted by 12 . This describes the execution according to 1a and 1b the area between radial plane ER-10.1 and segment side surface 9.1 or radial plane ER-10.2 and side surface 9.2.

In the illustrated first embodiment for the tilting segments 3, the segment side surfaces 9.1, 9.2 pointing away from one another in the circumferential direction are characterized by a flat surface, which is characterized by a flat surface 14.1, 14.2. The segment side surfaces 9.1 and 9.2 are arranged parallel to one another and the contour or profile describing the segment side surface 9.1, 9.2 is free of any change in the view of the Y-Z plane in the direction of extension in the longitudinal direction, i.e. viewed parallel to the bearing axis LA.

The segment side surfaces 9.1 and 9.2, which point towards one another in the circumferential direction, of two adjacent tilting segments 3 arranged at a distance from one another in the circumferential direction delimit a so-called segment pocket 13 in the circumferential direction, in which, as in 1b Schematically simplified, a cooling volume flow 16 is induced by the shaft rotation and can thus be brought closer to the range of the maximum temperature 15 on the tilting segment 3 .

1c shows an embodiment of a tilting segment 3 according to FIG 1a and 1b with parallel segment side surfaces 9.1, 9.2, which point away from each other in the circumferential direction in a perspective view. The bearing surface 5 and the individual segment edges 10.1 and 10.2 can be seen. It is evident from this that this is a particularly simply constructed component.

The one in the 1a Illustrated design of the tilting pad bearing 1 shows tilting pads 3, 3.2 to 3.5 with the same design. However, an embodiment (not shown here) with a differently designed geometry of the segment side surfaces on the individual tilting segments is also conceivable.

The 2 shows another second embodiment of a tilting segment 3, in which the segment side surfaces 9.1 and 9.2 are concavely curved in a perspective view. The bearing surface 5 can also be seen here, as well as the partial area 11 set back compared to a theoretical radial plane EA-10.1 or EA-10.2, which can be described by the concave curvature between the segment edge 10.1 or 10.2 and the radial outer surface 6. The concavely curved surface is denoted by 17.1, 17.2.

3 shows a combination of the versions of the geometries of the segment side surfaces 9., 9.2 according to 1 and 2 . The individual segment side surface 9.1, 9.2 is characterized by a sequence of a concavely curved surface 17.1, 17.2 and a flat surface 14.1, 14.2 from the bearing surface 5 in the direction of the radial outer surface 6 on the tilting segment. The individual surfaces 14.1, 14.2 and 17.1, 17.2 are characterized by a constant profile in the longitudinal direction. The flat surfaces 14.1 and 14.2 run radially here, for example, but can also—not shown here—be aligned parallel to one another.

The 4a and 4b show the integration of a tilting pad 3 based on a section of a tilting pad bearing 1 according to FIG 3 . 4b shows the eddy current forming in the segment pocket 13 and a supply device 18 for cooling oil, in particular fresh oil.

The in the 1 until 4 The embodiments shown show tilting segments 3, which are preferably constructed symmetrically with respect to a central plane and have segment side faces 9.1 and 9.2 of identical geometry in terms of geometry. This training can be used independently of the direction of rotation.

Also conceivable, but not shown here, is the different design of the segment side surfaces of a single tilting segment 3, for example from a combination of one of the versions according to FIG 1 until 4 for a segment side face 9.1 or 9.2 and, for example, a conventional configuration with an opposite segment side face 9.2 or 9.1 lying in the radial plane, for example EA-10.1 or EA-10.2. 5 shows an example of an embodiment with a segment side surface 9.1, which is designed as a flat surface and runs in the installed position in a tilting pad bearing in relation to the bearing axis in the radial direction, while the segment side surface 9.2 is designed as a flat surface, which is opposite to a through the bearing axis in the installed position and a Perpendicular to this plane, which is characterized by the respective edge, here the segment edge 10.2, is set back.

Furthermore, it is conceivable to design the individual tilting pads 3 of a tilting pad bearing 1 differently from one another with regard to the design of the segment side surfaces 9.1 and 9.2, so that different types of tilting pads can be used in one bearing. 6 shows an example of an embodiment with five tilting segments 3.1 to 3.5, with the tilting segments 3.1 to 3.3 and the tilting segments 3.4 and 3.5 being of the same design. The tilting segments 3.1 to 3.3 are, for example, analogous to the tilting segments in 2 formed, while the tilting segments 3.4 and 3.5 according to 5 are executed.

Reference List

1

tilting pad bearing

2

bearing housing

3, 3.2 to 3.5

tilting segment

4

bearing bore

5

storage area

6

radial outer surface

7

wing

8th

inner circumference

9.1,9.2

segment faces

10.1, 10.2

segment edges

11

subarea

12

setback

13

segment pocket

14.1, 14.2

flat surface

15

Maximum temperature area

16

cooling oil flow

17.1, 17.2

concave curved surface

18

feeding element

L.A

bearing axis

ER-10.1; ER-10.2

radial plane

X,Y,Z

directions coordinate system

W

Wave

r2-l, r3-A

radii

QUOTES INCLUDED IN DESCRIPTION

This list of documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• CN 102518670A [0005]
• DE 19514830 C2 [0007]
• JP 5026230 A2 [0007]
• JP 58180815 A2 [0008]
• WO 19163162 A1 [0009]
• JP 2019056429 A [0011]
• US9874247 [0012]
• JP 2016191402 A2 [0012]
• JP 6325915 B2 [0012]
• WO 14208196 A1 [0012]
• JP 6304471 B2 [0012]
• US9739310 [0012]
• US8834032 [0012]
• JP 4930290 B2 [0012]
• KR 100799546 B1 [0012]
• JP 2009030704 A2 [0012]
• US 9611886 [0012]
• US9759257 [0012]
• DE 112017001058 T5 [0013]
• JP 2017141882 A2 [0013]
• JP 2017026089 A2 [0013]
• KR 100817220 B1 [0013]
• JP 2004197890 A2 [0013]
• EP 2762735 A1 [0013]
• US2019024707 [0014]
• EP 2971821 B1 [0014]
• CN 202867564 U [0014]
• JP 9032848 A2 [0014]
• WO 19142383 A1 [0014]
• EP 3067577 A1 [0015]
• US 9618048 [0015]
• JP 6101135 B2 [0015]
• CN 102966830A [0015]
• EP 2588767 B1 [0015]
• US5738447A [0015]
• US2019277338A [0015]
• CN 205780314 U [0015]
• CN 108591245 [0015]

Claims (13)

Tilting pad bearing (1) for supporting a shaft or axle, comprising a bearing housing (2) with a bearing bore (4) aligned along a bearing axis (LA) and at least two movable relative to the bearing housing (2) and spaced apart from the bearing axis (LA) in the circumferential direction these spaced-apart tilting segments (3, 3.1, 3.2, 3.3, 3.4, 3.5), the individual tilting segment (3, 3.1, 3.2, 3.3, 3.4, 3.5) each having a radially inner bearing surface (5) and a radially outer surface ( 6) for support on a bearing surface (7) on the bearing housing (2) and has segment side surfaces (9.1, 9.2) connecting this to one another and pointing in the circumferential direction to the adjacent tilting segment (3, 3.1, 3.2, 3.3, 3.4, 3.5) and the transition between Bearing surface (5) and individual segment side surface (9.1, 9.2) describes a first and a second segment edge (10.1, 10.2) on the tilting segment (3, 3.1, 3.2, 3.3, 3.4, 3.5); characterized by ; that at least one of the segment side surfaces (9.1, 9.2) of an individual tilting segment (3, 3.1, 3.2, 3.3, 3.4, 3.5) pointing in the circumferential direction in the installed position has at least a partial area, viewed in the direction of extension from the bearing surface (5) to the radial outer surface (6). , which is set back with respect to a theoretical plane (ER10.1, ER-10.2) that can be described by the respective segment edge (10.1, 10.2) in relation to a theoretical plane (ER10.1, ER-10.2) that can be described by the bearing axis (LA) and a perpendicular to this in the radial direction. Tilting pad bearing (1) after claim 1 , characterized in that the individual segment side surface (9.1, 9.2) viewed in the longitudinal direction of the tilting segment (3, 3.1, 3.2, 3.3, 3.4, 3.5) has a constant profile or is characterized by a continuous progression. Tilting pad bearing (1) after claim 1 or 2 , characterized in that the at least one segment side surface (9.1, 9.2) of an individual tilting segment (3, 3.1, 3.2, 3.3, 3.4, 3.5) is viewed at least in a partial area of its extension, preferably completely between the bearing surface (5) and the outer surface (6). can be written on by a flat surface, which is at an angle in the range of 20° to 45° theoretical through the bearing axis (LA) and a perpendicular to this plane (ER-10.1, ER-10.2) is aligned. Tilting pad bearing (1) after claim 3 , characterized in that the segment side faces (9.1, 9.2) pointing away from one another of an individual tilting segment (3, 3.1, 3.2, 3.3, 3.4, 3.5) are aligned at least partially, preferably completely, parallel to one another. Tilting pad bearing (1) according to one of Claims 1 until 4 , characterized in that an individual segment side surface (9.1, 9.2) of an individual tilting segment (3, 3.1, 3.2, 3.3, 3.4, 3.5) is viewed at least in a partial area of its extension between the bearing surface (5) and the outer surface (6), preferably completely can be described by a concavely curved surface (17.1, 17.2). Tilting pad bearing (1) after claim 5 , characterized in that the curvature of the concavely curved surface (17.1, 17.2) is at least partially arcuate, cylindrical or elliptical or is characterized by at least one or a sequence of radii. Tilting pad bearing (1) according to one of the preceding claims, characterized in that the two segment side faces (9.1, 9.2) pointing away from one another and aligned in the circumferential direction of a single tilting pad (3, 3.1, 3.2, 3.3, 3.4, 3.5) are symmetrical with respect to a plane which characterized by the bearing axis (LA) and a perpendicular through the middle of the extent of the bearing surface (5) in the circumferential direction. Tilting pad bearing (1) according to one of the preceding claims, characterized in that the segment side surfaces (9.1 or 9.2) pointing in the same direction of a plurality, preferably all individual tilting pads (3, 3.1, 3.2, 3.3, 3.4, 3.5) are of identical design. Tilting pad bearing (1) according to one of the preceding claims, characterized in that the two side surfaces (9.1, 9.2) of a single tilting pad (3, 3.1, 3.2, 3.3, 3.4, 3.5) pointing away from one another and in the installed position in the circumferential direction extend in the direction of extension from the Viewed from the radial outer surface (6), the bearing surface (5) has at least a partial area which is in relation to a theoretical plane (ER-10.1, ER-10.2) is set back. Tilting pad bearing (1) according to one of Claims 1 until 8th , characterized in that the other of the two segment side surfaces (9.2 or 9.1) of a single tilting segment (3, 3.1, 3.2, 3.3, 3.4, 3.5) viewed in the direction of extension from the bearing surface (5) to the radial outer surface (6) in a through the bearing axis (LA) and lies perpendicular to this plane which can be described in the radial direction. Tilting segment bearing (1) according to one of the preceding claims, characterized in that the individual tilting segments (3, 3.1, 3.2, 3.3, 3.4, 3.5) are designed differently with regard to the segment side surfaces (9.1, 9.2), in particular in the installed position the load segments compared to the non -Load segments are designed differently. Tilting pad bearing (1) according to one of the preceding claims, characterized in that the individual tilting pad (3, 3.1, 3.2, 3.3, 3.4, 3.5) is supported with the radial outer surface (6) directly on the inner circumference of the bearing housing (7), the radial outer surface (6) of the individual tilting segment (3, 3.1, 3.2, 3.3, 3.4, 3.5) can be described by a radius which is smaller than the inner radius of the bearing housing (2). Tilting pad bearing (1) according to one of the preceding claims, characterized in that in a segment pocket, which is delimited by the mutually facing segment side surfaces (9.2, 9.1) of two mutually adjacent tilting segments (3, 3.1, 3.2, 3.3, 3.4, 3.5), a device (18) for supplying fresh oil or cooling oil is arranged or opens into this through the bearing housing (2).

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