Squeezing oil film damper

Abstract

The invention relates to a squeeze film damper (10) having an inner ring (11) and an outer ring (12), the inner ring (11) and the outer ring (12) being able to be tensioned against each other and / or variably positioned. In a method for producing a squeeze film damper (10), elements of the squeeze film damper (10) are tensioned or positioned, the first element being an inner ring (11) and the second element being an outer ring (12).

Description

Technical Field

[0001] The present invention relates to an extrusion film damper and a method for manufacturing or operating the extrusion film damper, wherein the extrusion film damper is used particularly in bearings. Background Technology

[0002] Squeeze film dampers are used, for example, in electric motors. Electric motors are, for example, motors or generators. By using squeeze film dampers, particularly in conjunction with the bearings of the motor, the rotor dynamics design of a rotating electric motor can be influenced. Especially in fast-rotating machines, i.e., fast-rotating motors, the occurrence of the natural frequencies of the rotor bearing system within the operating range must be considered within the scope of rotor dynamics machine design. This can impose limitations on machine operation because operation at or near the natural frequency can lead to large amplitudes, which are generally undesirable through standardization or due to the need to ensure operational safety. If vibrations cannot be adequately prevented or damped, the machine can only be used within a limited operating speed range. Rotor dynamics design, for example, is specifically tailored to the requirements of the operating speed range for a particular project or application. If this operating speed range is to be adapted (moved or extended), the dynamic system consisting of the rotor, sliding bearings, and supports needs to be re-coordinated. This is associated with significant time and resource costs, which, in supply cases, must already be experienced, significantly extending the duration of supply processing and being disadvantageous. Furthermore, rotor bearing systems, such as those in motors with rotors and stators, cannot be optimized to a degree using conventional sliding bearings, i.e., to achieve significant robustness relative to changes in the operating speed range. This often results in additional project-specific and / or application-specific design flows. Rotor bearing systems can be improved using squeeze film dampers. The bearings used are, for example, ball bearings or sliding bearings.

[0003] A bearing support structure is known from US 4,453,783 A, in which an outer bearing ring is located within a support ring, which is surrounded by an outer damping ring to form an oil damping chamber therebetween. Protruding flanges are present at the ends of the support ring, on which the ends of rings made of rods are respectively fastened. These rod rings surround the outer damping ring and are fastened at the distal end of the outer damping ring to the other end of the rod. The inner end of the damping ring is supported by a fastening flange through a frustoconical element having a through-hole for the rod.

[0004] A squeezed-film damper is known from US 9,890,810 B2, comprising a bearing housing as an inner ring arranged radially outward of a bearing that rotatably supports a rotating shaft. Furthermore, an outer ring is arranged radially outward of the bearing housing, a squeezed film formed by the circulation of a viscous material is present, wherein fluid passes through a gap in the radial direction between the bearing housing and the outer ring, and a coupling pin is present, which couples the bearing housing and the outer ring to each other. In a cross-section perpendicular to the axial direction of the rotating shaft, the coupling pin has higher rigidity in the vertical direction than in the horizontal direction. Summary of the Invention

[0005] The objective of this invention is to improve a squeeze film damper.

[0006] The solution to the task is derived in the extrusion film damper according to claim 1, in the motor according to claim 14, or in the method according to claim 15. Other design solutions are derived, for example, according to claims 2 to 13, 16, and 17. Features of these design solutions, or other design solutions and examples described below, can also be combined with each other.

[0007] An extrusion film damper has an inner ring and an outer ring, wherein the inner ring and the outer ring are connected by means of rods, wherein at least one of the rings, i.e., particularly the inner ring or the outer ring, has a flange, and wherein each rod is connected only to the flange. Therefore, an axially compact structural form is possible, for example. Axial forces can also be transmitted, for example. The rods are particularly implemented as elastic elements, i.e., particularly as rod springs. The rods particularly have a circular or oval cross-section.

[0008] In the design of the squeeze film damper, different rods or rod groups (especially sequentially arranged circumferentially) are alternately connected to different flanges, particularly on different end sides of the squeeze film damper, inner ring, or outer ring, where the rods are connected only to the flanges. This means that the connection to the flange is achieved on one side of the rod, and the connection to the flangeless end side is achieved on the other side of the rod. For example, the end side of the rod is positioned on the flange of one ring in the ring, and the other end of the rod is positioned on the opposite end side of another ring in the flange gap of that other ring.

[0009] In the design of the squeeze film damper, the squeeze film damper is cross-integrated into the bearing. The inner and outer rings have completely or primarily the same axial position.

[0010] In the design scheme of the squeeze film damper:

[0011] -Inner ring and outer ring or

[0012] -Inner ring only or

[0013] -Outer ring only

[0014] It has flanges. One or more flanges are particularly toothed. A single rod is connected to only one of the flanges. In particular, the squeeze film damper has axially oriented rods arranged in a circular pattern, wherein the rods, at least partially positioned side by side, are connected to different flanges.

[0015] The connection of multiple rods or a single rod specifically involves one end region of the rod's end areas. The end region of the rod may have threads, for example, onto which a screw can be screwed. The other end region of the rod may have a head as a stop, for example. Between the end regions of the rod, the rod is particularly unthreaded; that is, there are no threads between the end regions.

[0016] In the design, the squeeze film damper with inner and outer rings has a shape in which the inner and outer rings are axially positioned relative to each other by means of rods. Axial positioning relative to each other by rods specifically implies independent positioning. The rods are particularly members with circular, angular, oval, or other cross-sections. One or more rods are particularly implemented as one or more rod springs. Rod springs are particularly members whose elastic properties are used for elastic action. With the inner ring fixed in axial positioning relative to the outer ring, axial force can be transmitted. Axial here means along an axis and / or in the direction of the axis. Here, the axis is particularly the axis of a bearing or the axis of rotation. These rods are particularly threaded. The threads are particularly in the area of ​​the rod or the individual rods that is not subjected to alternating mechanical loads during operation, i.e., particularly not subjected to elastic action. These rods are particularly guided by notches in the outer ring.

[0017] In particular, the inner and outer rings have end sides. These rods are axially oriented and have end regions. The first end region of the rod is, for example, an end head, and the second end region is, for example, threaded, in which a screw is screwed. For example, the rod can also have threads with screws at each end region.

[0018] In the design of the squeeze film damper, a rod, or multiple rods, has its first end region connected to the inner ring on its end side, while its second end region is connected to the outer ring. Therefore, the rod rests against the inner ring with one end region on its axial end side and against the outer ring with another end region on its other axial end side. This configuration can be used for multiple rods.

[0019] In the design of the squeeze film damper, single rods or groups of rods are alternately connected to the inner or outer ring on the end side.

[0020] In the design of a squeeze film damper, the inner and outer rings can be tensioned relative to each other, i.e., tensioned and / or variably positioned relative to each other. Variable positionability involves the positioning of the inner and outer rings relative to each other. This positioning, for example, involves axial and / or radial positioning. Therefore, in a squeeze film damper, the inner and outer rings can be tensioned and / or variably positioned relative to each other. This tensioning and / or positioning is achieved, in particular, through the interlacing of elements used for tensioning and / or positioning. The inner or outer ring can, in particular, accommodate bearings, especially those for motors. The motor is, for example, a rapidly rotating motor with speeds ranging from 1000 to 30000 U / min. Through the feasible tensioning or positioning, the operating speed range of the machine (motor) can be adapted. If this operating speed range is to be adapted (moved or extended), the dynamic system consisting of the rotor, sliding bearings, and supports needs to be re-coordinated. This can now be achieved by changing the tensioning and / or positioning. If the inner and outer rings are positioned relative to each other, then that positioning can be achieved in such a way that the rings are either stress-free relative to each other or taut relative to each other.

[0021] In the design of a squeeze film damper, a rod is provided to connect an inner ring to an outer ring. The inner ring is tensioned relative to the outer ring, particularly axially, by means of the rod, or can be tensioned and / or positioned, or can be variably positioned. Different and / or identical rods can, for example, have different and / or identical cross-sections. The cross-sections are, for example, circular, angular, or oval. The rod can produce an elastic effect. Therefore, the rod is a type of elastic element and can thus also be called a spring rod or elastic element. Furthermore, the rod is particularly used to achieve tension or positioning of the inner and outer rings, especially cross-tension or positioning. With a preload, these rods are particularly loaded with tension or preloaded. Therefore, the rigidity of the connection between the inner and outer rings of the squeeze film damper can be changed.

[0022] In the design of the squeeze film damper, the inner and / or outer rings are open and / or closed rings, wherein, in particular, multiple open rings can be joined together to form a closed ring. The squeeze film damper is also segmented into two half-rings, for example. These segments can be joined together to form a closed ring. These segments are, for example, threaded together with each other. By segmentation, bearings can be integrated into the squeeze film damper, for example. The squeeze film damper includes, for example, entirely or partially, a bearing, which is, for example, a sliding bearing or a rolling bearing. The squeeze film damper can be positioned, for example, together with the bearing in a bearing housing. In this design, the squeeze film damper is part of the bearing. Therefore, generally speaking, the present invention relates not only to squeeze film dampers but also to bearings (e.g., rolling or sliding bearings) having squeeze film dampers.

[0023] In the design of the squeeze film damper, the inner ring and / or outer ring are separable or detachable. This facilitates integration into and / or connection to the bearing, particularly structurally. The inner or outer ring can have a lower annular segment and an upper annular segment, which are joined together to form a complete circle. The lower annular segment is the part facing the bearing, bearing housing, or motor fastened to a base (e.g., a support or chassis). The upper annular segment is correspondingly the part facing away from this fastening.

[0024] In the design of the squeeze film damper, a first number of rods are configured to pull the outer ring in a tensile direction along a first axial direction, and a second number of rods are configured to pull the outer ring in a tensile direction along a second axial direction, wherein rods and / or groups of rods with different potential tensile directions alternate. This alternation results in a cross. The tensile directions are particularly opposed and additionally parallel to the axis of rotation of the motor or the axis of rotation of the bearing. The rods can utilize their elastic action to construct a type of spring cage. Furthermore, the rods can be circularly positioned with their axes parallel to the support axis. Thus, it is possible to realize a squeeze film damper with a cross spring cage including a preloaded elastic element and / or variable stiffness, wherein the spring cage is particularly integrated into the bearing housing in its structural form, or integrated, i.e., particularly completely or partially surrounding the bearing, such as a sliding bearing. The cross connection between the inner and outer rings enables small internal constraint forces and thus achieves the most ideal radial guidance of the rings relative to each other without tilting. The different, at least potentially different, tensile force directions between the inner and outer rings, achieved through a cross-connection, prevent the inner ring from tilting relative to the outer ring. The transmission of axial force is particularly effective through form-fitting.

[0025] In the design of the squeeze film damper, the rod has a surface layer, which is produced by a surface coating and / or a surface treatment. The surface layer is produced, for example, by nitriding the matrix of the rod made of 42CrMo4 material. This ensures sufficient anti-biting safety in the event of repeated engagement between the rod and the ring, i.e., the outer or inner ring.

[0026] In the design of the squeeze film damper, the rod is made of different materials.

[0027] In the design of the squeeze film damper, the rod has a material with higher flexural alternating fatigue strength than the material used to construct the ring.

[0028] In one design of the squeeze film damper, the inner ring has a U-shaped profile, with the outer ring at least partially extending into this profile. In another design of the squeeze film damper, the outer ring also has a U-shaped profile, with the inner ring at least partially extending into this profile. Here, the profile is derived from successive cross-sections. The first cross-section of the ring has, for example, a first L-shape, and a subsequent second cross-section of the ring has a mirrored second L-shape. Through mirroring, the two overlapping L-shapes actually create a U-shape. The U-shape of the ring is not necessarily created by a single cross-section, but rather by comparing successive cross-sections of the ring in a shadow-projection manner. This order of the different cross-sections makes intersections possible.

[0029] Therefore, a compact structural form can be achieved. Furthermore, it is possible to achieve tensioning and positioning from the inner ring to the outer ring (or vice versa) in a simple manner.

[0030] In this embodiment, the inner ring has axial end sides. On each end side, the inner ring has toothed flanges. The teeth point radially outward. Each tooth is distributed on the circumference of a circular flange. The teeth allow for an L-shaped cross-section of the ring. The teeth on one end side are offset in their circular position relative to the teeth on the other end side. The teeth have holes through which rods are threaded. Furthermore, the rods are guided through holes in the outer ring. The outer ring has multiple holes for the rods to pass through, wherein these holes extend axially parallel. Due to the offset of the teeth on the end sides, the inner ring is pulled or positioned towards the outer ring (or vice versa) in a first axial direction by the rod in the region of the teeth on the first end side. Similarly, by offsetting the teeth on the end sides, the inner ring is pulled or positioned towards the outer ring (or vice versa) in a second axial direction opposite to the first axial direction by the rod in the region of the teeth on the second end side. This achieves a cross-tension, particularly from the inner ring to the outer ring.

[0031] In the design, individual rods or rod assemblies can be alternately pushed into or pushed into the inner and / or outer rings from either the left or right (i.e., from the opposite end). This alternation allows for the construction of intersecting spring cages. The outer ring can thus be tensioned or positioned relative to the inner ring because it is alternately stretched or positioned axially parallel in opposite directions via fan-shaped (annular segments). Positioning, especially axial positioning, can be variable because the effective length of the rod can be shortened or lengthened by the nut when the rod is implemented as a screw. In the design of rods with elastic action, the rod has an elastic length, wherein the elastic length remains constant regardless of the position-dependent effective length of the rod.

[0032] In the design of the squeeze film damper, the bearing is nested within the squeeze film damper. The bearing (especially a sliding bearing) can be threaded to the inner ring, pressed into the inner ring, or integrated into the inner ring, for example.

[0033] In the design of this extrusion oil film damper, a bearing is provided, which is in particular a sliding bearing and specifically supports the rotor of the motor.

[0034] In the design of the extrusion film damper, the extrusion film damper is integrated, or can be integrated, into the bearing housing. Therefore, a compact structural form can be achieved.

[0035] In the design of the squeeze film damper, the tension and / or positioning of the inner and outer rings can be adapted. This is achieved, for example, by changing the tension on the rod or changing the effective length of the rod. If the rod has a threaded connection, for example, the tension on the screw can be changed. In other designs, different rods can also be used to adapt the tension, or one or more rods can be replaced by one or more other rods, especially those with other materials and / or other shapes. Thus, for example, it is possible to select one or more rods with different cross-sections in terms of shape or size.

[0036] In the design of the squeeze film damper, at least one rod is replaceable and / or the rod has at least one different elastic action. This can, for example, positively influence the frequency response of the motor, by expanding or adapting to a frequency range where inherent vibrations do not occur.

[0037] The electric motor, such as a synchronous or asynchronous motor, particularly has a first bearing and a second bearing. The first bearing is located, for example, on the drive side of the motor, which is particularly a motor or generator, and the second bearing is located, for example, on the operating side of the motor. At least one of the bearings has a squeeze film damper, or is combined with and / or connected to it. The squeeze film damper has one of the embodiments or features of the squeeze film damper described herein.

[0038] According to a method for manufacturing a squeeze film damper, the elements of the squeeze film damper are tensioned and / or variably positioned, wherein the first element is an inner ring and the second element is an outer ring. A rod can be used for tensioning or positioning. To change the tension, the tensile load on the rod can be changed. Furthermore, to change the tension, the rod can be replaced, wherein the new rod differs from the replaced rod. The difference specifically relates to the elastic properties of the corresponding replaced rod. For positioning, the effective length of the rod can be changed.

[0039] In this design scheme, at least one rod is replaced to change the elastic action and / or position, and / or for at least one rod, the preload is changed and / or the effective length of the rod is altered. In one type of screw implementation, the effective length of the rod is determined by the position of the nut. Any portion of the rod protruding beyond the nut is ineffective.

[0040] In the design scheme of this method, a squeeze film damper of the type described is used.

[0041] The squeeze film damper, for example, can maintain or improve hydrodynamic sliding bearings. Such bearings are used, for example, in electric motors. Hydrodynamic sliding bearings, as a type of bearing, are retained or supplemented between rotating and stationary components of a system, such as an electric motor. Furthermore, additional bearings are inserted into the stationary components, using the squeeze film damper. The squeeze film damper can therefore be understood as a support for the bearings of an electric motor, i.e., the rotating bearings. By means of the described squeeze film damper, improved decoupling of the rotor bearing system from the support, i.e., the base for mounting the motor, can be achieved, and the influence of the oil film coefficient can be reduced. Examples of support, besides the base, include frames, housings, etc.

[0042] When using conventional sliding bearings, the natural frequency of a rotor bearing system is decisively determined by the oil film coefficient, which is related to the rotational speed. With the additional use of a squeeze film damper, the rotor support is designed to be significantly softer, thus physically creating only a weak coupling between the rotor and the support. Furthermore, due to this weak coupling, the effect of the oil film coefficient becomes secondary. The rotor increasingly behaves as if it were in a "free-free" support. This type of support allows for a large gap between natural frequencies, which is now also independent of the operating speed and its associated oil film coefficient.

[0043] Additional damping components and / or spring assemblies can be inserted through the rod of the squeeze film damper. The squeeze film damper can be physically considered a spring-dampening system. This, in addition to decoupling the rotor sliding bearing system, also enables damping of the natural frequencies that occur, which can potentially benefit the operating characteristics of rotating machines.

[0044] Using metal spring cages in squeeze film dampers can potentially increase axial structural space. This can be avoided in the proposed squeeze film damper by its achievable small axial structural space. In this squeeze film damper, the rods (rod springs) are alternately pushed in from the left or right, creating a crossed spring cage. This arrangement is particularly useful for designs where the bearing does not need to be axially longer. Longer axial structures typically lead to deterioration of rotor dynamics and higher material usage. Furthermore, the crossed arrangement of the rod springs provides the advantageous characteristic of setting pure radial motion without tilting the bearing support.

[0045] In the design scheme of the extrusion film damper, or in the design scheme of this method, the extrusion film damper can be centered. This is manifested in positioning. By using a targeted preload on the rod (rod spring), which is generated by the offset between the lower and upper annular segments, the elastic compression of the spring cage caused by gravity can be avoided or compensated, which will have a positive impact on the linear characteristics of the extrusion film damper.

[0046] In the design of this squeeze film damper, or in the design of this method, the settling capability of the elastic element, i.e., the rod spring, is achieved, wherein the elastic element, i.e., the rod spring, provides enhanced variability in different aspects (individually or collectively):

[0047] ● By adapting its quantity, diameter, and / or profile, its stiffness can be changed very easily, and its properties can be predicted quite well.

[0048] ● The system design, in particular, utilizes end-mounting to ensure the removability of the bar springs. The advantage of this is that these bar springs can be replaced with other springs if needed, or...

[0049] When the machine's operating conditions change, it may be able to respond to previously unknown faults in the system.

[0050] ● By implementing the spring as a separate, detachable structural element, different materials (e.g., spring steel, 50CrV4, 51CrV4, 100Cr6, 51CrMoV4, 100CrV4) and different manufacturing methods (e.g., grinding, hardening, tempering, shot peening) can be used for the spring, which are particularly suitable for use in the spring; thus, better material utilization and smaller structural dimensions of the spring can be achieved.

[0051] The described squeeze film damper enables improved robustness in machine rotor dynamics design, resulting in significantly improved applicability with lower design costs. A space-saving arrangement of the spring cage within standard bearing inserts is possible without additional axial structural space. In particular, variable spring stiffness within the spring cage can be achieved through the removability and replaceability of the springs.

[0052] In the design of the extrusion film damper, a type of spring cage is constructed using rods. These rod springs are arranged parallel to their axes about the axis of rotation. The rod springs provide both radial and axial stiffness. The rods are replaceable. These rods can be replaced with the routine maintenance required for bearings, without disassembling the entire machine.

[0053] In the design of the squeeze film damper, the squeeze film damper, particularly regarding the cage also constructed by a rod, has at least one of the following functions or characteristics:

[0054] ● A radially adjustable rigidity connection between the outer and inner rings, featuring a squeeze film damper, achieved via a rod spring, is particularly suitable for...

[0055] The centering of the outer and inner rings and / or the targeted preload of each rod spring are used to set the gap as evenly as possible across the entire circumference.

[0056] o Provides radial support and / or for static and dynamic force transmission

[0057] Components are axially supported and / or positioned relative to each other;

[0058] A rod spring with a detachable connecting device / method is installed in the inner and outer rings, wherein,

[0059] By utilizing the selected material pair (e.g., 51CrV4 and CIO) and / or a surface layer applied to the spring, disassembly is simplified and additional fatigue strength of the spring is achieved (e.g., through surface hardening and / or shot peening). Attached Figure Description

[0060] Features of the various claimed or described objects or methods can be readily combined with each other. The invention is illustrated and explained in more detail below with the aid of the accompanying drawings. Features shown in the drawings can be combined to form new embodiments without departing from the invention. Elements of the same type have the same reference numerals. See:

[0061] Figure 1 Two graphs showing the frequency response of the motor are provided.

[0062] Figure 2 This shows a partial cross-section of the squeeze film damper in the bearing housing.

[0063] Figure 3 A perspective view of the squeeze film damper is shown.

[0064] Figure 4 Another portion of the cross-section of the squeeze film damper is shown, and

[0065] Figure 5 A perspective view of the two-piece inner ring is shown. Detailed Implementation

[0066] according to Figure 1The illustrations show a first graph 1 and a second graph 2, where both graphs show the frequency response with respect to rotational speed. Rotational speed is plotted on axis 3 and frequency on axis 4. Frequency relates to the system of rotor, bearing, and support (base). To measure this frequency, a sensor can be mounted, for example, on the rotor or bearing housing. However, frequency can also relate to the relative motion between the bearing and the rotor. Rotational speed relates to the rotation of the motor's rotor or the motor's bearing. Shaded areas 5 in the graphs respectively indicate areas of safe behavior where the inherent frequency is not excited. The left graph, or upper graph 1, relates to a system with a sliding bearing. The right graph, or lower graph 2, relates to a system with a sliding bearing equipped with a squeeze film damper. It can be seen that the range of safe operation of the system is improved by using a squeeze film damper. The system has at least one motor with a supported rotor.

[0067] according to Figure 2 The view shows a partial cross-section of a squeeze film damper 10 in a bearing housing 24. The squeeze film damper 10 has an inner ring 11 and an outer ring 12. The inner ring 11 of the squeeze film damper 10 serves as a sliding bearing support. The sliding bearing has a sliding bearing section 27 or more sliding bearing sections. The sliding bearing is used to support a rotor 26 or rotor shaft of an electric motor, which is not shown in detail. The rotor shaft 26 has an axis 31, in which a first axial direction 32 and a second axial direction 33 are shown. The inner ring 11 is constructed with a U-shaped profile 30 by the position of teeth alternately distributed on different end sides, into which the outer ring 12 extends. Opposite toothed flanges 20 are constructed on the end sides 28 and 29 of the inner ring 11 by the U-shaped profile 30, the toothed flanges being offset relative to their angular positions with respect to the different end sides. The corresponding end side flanges 20 have teeth. The teeth of the opposite end side flanges are thus offset along an arc, i.e., alternately distributed opposite each other along the circumference. Therefore, it is possible to pass through rod 13 or through multiple rods (as in...). Figure 3 As shown in the diagram), the outer ring 12 can be alternately pulled toward the inner ring 11 along the first direction 32 or variably positioned, and via an additional rod (in Figure 2 (Not shown) The inner ring 11 is pulled or variably positioned along the opposite second direction 33. This achieves tensioning or positioning of the inner ring 11 and the outer ring 12. The squeeze film damper gap 23 is located between the inner ring 11 and the outer ring 12. The bearing housing 24 is sealed via a seal 25. In addition, anti-torsion elements 66 and 67 are shown.

[0068] according to Figure 3The illustration shows a perspective view of the squeeze film damper 10. The squeeze film damper 10 has a lower annular segment (part) 22 and an upper annular segment (part) 23. The lower part 22 and the upper part 23 are releasably threaded together. A bearing joint 34 is constructed between parts 11 and 12. The cage constructed by the rods is thus divided into two halves by the bearing joint 34. This allows for easy disassembly and / or for introducing offset and thus introducing preload. The visible end flange of the inner ring has teeth 20 and 21. Through these teeth, such as tooth 20, rods 13, 14, 15, and 16 are guided by the tooth set to connect the outer ring 12 to the inner ring 11. In addition to the teeth, rods 17, 18, and 19 connect the inner ring 11 to the outer ring 12 from another opposite, invisible end of the inner ring 11. The rods are constructed to provide an elastic action and can therefore also be called rod springs. The rod sets are crossed. Figure 2 and Figure 3 The view exemplarily illustrates a sliding bearing insert with a bearing bush and an integrated squeeze film damper.

[0069] according to Figure 4 The view shows another portion of the cross-section of the squeeze film damper. Axis axes 51 and 52 can be found in this diagram. Furthermore, an outer ring 12 and an inner ring 11 are shown. These are connected to each other by means of a rod 13. The inner ring 11 has a flange 68. This results in an L-shaped cross-section for the inner ring. Additionally, a first end region 43 of the rod 13 with an end head 45 and a head widening portion 48 and a second end region 44 with a nut 46 and a washer 47 are shown, wherein the nut 46 is screwed onto a thread (not shown) in the end region 44. The inner ring 11 has a mating portion 70 in a mating region 41 for receiving the rod 13. The outer ring 12 has a mating portion 71 in a mating region 42 for receiving the rod 13. A spring region 40 exists between these mating regions. In this spring region 40, the rod 13 is received in a recess 50 of the outer ring 12. An elastic action of the rod 13 can be formed in this spring region 40, wherein a free space 64 is provided for this purpose. The inner ring 11 has an annular channel 69 for supplying oil. Seals 37 and 38 are provided for sealing. The figure also shows bearing working surfaces 53, 54, and 55, which can be constructed in conjunction with a squeeze film damper, especially when using sliding bearings. End faces are characterized by arrows 57 and 58. Figure 4 Arrow 57 points to the left end face of the inner ring 11 and arrow 56 points to the right end face of the outer ring 12. The left-side support surface of the inner ring 11, according to this figure, is at least partially formed by a flange 68. Furthermore, by… Figure 4 It is known that the rod 13 connects the inner ring 11 and the outer ring 12 only via a flange. This flange is the flange 68 of the inner ring 11.

[0070] according to Figure 5The illustration shows a three-dimensional example of an inner ring 11, which is implemented in two parts. The inner ring 11 has a first portion 64 and a second portion 65. These portions are threaded together. Portions 64 and 65 are respectively ring segments or annular circles. The two portions 64 and 65 form the inner ring 11, which has flanges on both end sides. On the first end side, marked with arrow 57, the flange has teeth with teeth 58, 59, and 60. On the second end side, marked with arrow 56, the additional flange has teeth with teeth 61, 62, and 63. (See from...) Figure 5 As can be seen, the teeth on one end face are offset circumferentially from the teeth on the other end face. Therefore, it must be ensured, for example, that the connection between the inner and outer rings is achieved via a rod, such that the rod connects only to the flange. This also makes good accessibility of the rod on the end face possible. The connection between the rod and the outer ring is achieved in the area of ​​the tooth gap in the flange of the inner ring. This is, for example, in… Figure 3 Presented in the middle.

Claims

1. A squeeze film damper (10) having an inner ring (11) and an outer ring (12), wherein, The inner ring (11) and the outer ring (12) are connected by means of rods (13, 14, 15, 16, 17, ... 18, 19) are connected, wherein at least one of the rings (11, 12) has a flange (68), wherein each rod (13, 14, 15, 16, 17, 18, 19) is connected only to the flange (68).

2. The extrusion film damper (10) according to claim 1, wherein, The inner ring (11) and the outer ring (12) can be tensioned relative to each other, especially axially, and / or can be variably positioned by means of the rods (13, 14, 15, 16, 17, 18, 19), and / or different rods (13, 14, 15, 16, 17, 18, 19) or groups of rods are alternately connected to different flanges.

3. The extrusion film damper (10) according to claim 1 or 2, wherein, Rod (13, 14, 15, 16, 17, 18, 19) are configured to connect the inner ring (11) to the outer ring (12), wherein the inner ring (11) is connected by means of the rods (13, 14, 15, ...). 16, 17, 18, 19) are stretched axially relative to the outer ring (12).

4. The extrusion film damper (10) according to any one of claims 1 to 3, wherein, The inner ring (11) and / or the outer ring (12) are open rings and / or closed rings, wherein, in particular, the open rings can be joined together to form a closed ring.

5. The extrusion film damper (10) according to any one of claims 1 to 4, wherein, The inner ring (11) and / or the outer ring (12) are separable.

6. The extrusion film damper (10) according to any one of claims 1 to 5, wherein, A first number of rods (13, 14, 15, 16, 17, 18, 19) pull the outer ring (12) along the first axial tensile direction, and a second number of rods (13, 14, 15, 16, 17, ... 18, 19) Pull the outer ring (12) along the second axial tensile direction, wherein rods (13, 14, 15, 16, 17, 18, 19) and / or rod groups (13, 14, 15, 16) (17, 18, 19) with different tensile directions alternate.

7. The extrusion film damper (10) according to any one of claims 1 to 6, wherein, The rods (13, 14, 15, 16, 17, 18, 19) have a surface layer.

8. The extrusion film damper (10) according to any one of claims 1 to 7, wherein, The rod is made of different materials.

9. The extrusion film damper (10) according to any one of claims 1 to 8, wherein, The inner ring (11) has a U-shaped profile (30), and the outer ring (12) extends at least partially into the profile (30), or the outer ring (11) has a U-shaped profile (30), and the inner ring (12) extends at least partially into the profile (30).

10. The extrusion film damper (10) according to any one of claims 1 to 9, wherein, The squeeze film damper is provided for the bearing (27), wherein the bearing (27) is in particular a sliding bearing (27).

11. The extrusion film damper (10) according to any one of claims 1 to 10, wherein, The squeeze film damper (10) can be integrated into the bearing housing (24).

12. The extrusion film damper (10) according to any one of claims 1 to 11, wherein, Tightening can be adapted.

13. The extrusion film damper (10) according to any one of claims 2 to 12, wherein, At least one lever (13, 14, 15, 16, 17, 18, 19) is replaceable, and / or at least one of the levers (13, 14, 15, 16, 17, 18, 19) has a resilient function.

14. An electric motor having a first bearing and a second bearing, wherein, At least one bearing has a squeeze film damper (10) according to any one of claims 1 to 13.

15. A method for manufacturing an extrusion film damper (10), wherein, The elements of the squeeze film damper (10) are tensioned and / or variably positioned, wherein the first element is an inner ring (11) and the second element is an outer ring (12).

16. The method according to claim 15, wherein, To change the elastic action, replace at least one rod, and / or, in the case of one rod (13, 14, 15, 16, 17, 18, 19), at least change the preload, and / or change the effective length of the rod (13, 14, 15, 16, 17, 18, 19).

17. The method according to claim 15 or 16, wherein, Use the squeeze film damper (10) according to any one of claims 1 to 13.

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