CN117222819A - Radial foil bearing with overload protection and shaft displacement limiting mechanism - Google Patents

Radial foil bearing with overload protection and shaft displacement limiting mechanism Download PDF

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Publication number
CN117222819A
CN117222819A CN202280027282.7A CN202280027282A CN117222819A CN 117222819 A CN117222819 A CN 117222819A CN 202280027282 A CN202280027282 A CN 202280027282A CN 117222819 A CN117222819 A CN 117222819A
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CN
China
Prior art keywords
foil
radial
stop
bearing
shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202280027282.7A
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Chinese (zh)
Inventor
于尔根·希尔宾格
恩德雷·安杰尔
沃尔夫冈·布劳恩
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication date
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Publication of CN117222819A publication Critical patent/CN117222819A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/024—Sliding-contact bearings for exclusively rotary movement for radial load only with flexible leaves to create hydrodynamic wedge, e.g. radial foil bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0603—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion
    • F16C32/0607—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion the gas being retained in a gap, e.g. squeeze film bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C39/00—Relieving load on bearings
    • F16C39/02—Relieving load on bearings using mechanical means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/23—Gas turbine engines
    • F16C2360/24—Turbochargers

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Support Of The Bearing (AREA)

Abstract

The invention relates to a radial foil bearing (1) having overload protection and a shaft displacement limiting mechanism for limiting the radial displacement of a shaft (7) to be supported.

Description

Radial foil bearing with overload protection and shaft displacement limiting mechanism
Technical Field
The radial foil bearing is provided for pneumatically supporting the shaft, wherein a gas/air cushion is provided for carrying the shaft between the shaft and the radial foil bearing. The working principle is similar to that of a hydrodynamic plain bearing, except that the shaft is carried by a radial foil bearing through an air cushion rather than a liquid cushion of the hydrodynamic plain bearing. Common to both modes of operation is that the rotational movement of the shaft does not cause the formation of a load-bearing pad.
Background
Foil bearings differ from conventional pneumatic bearings in the flexible, resilient structure between the rotating shaft and the stationary housing member. By means of this feature, the foil bearing, although having a lower stiffness than conventional air bearings, can be adapted to air gap geometry changes, for example, due to misalignment of the bearing blocks or different thermal expansions of the shaft and the housing, so that in practice a higher operational reliability can be achieved in a wide variety of applications.
In order to form an air cushion for carrying the load, radial foil bearings generally have a cover foil in contact with the stationary shaft and a corrugated foil arranged radially between the cover foil and the outer ring of the bearing, which corrugated foil is elastically compressible in the radial direction. In principle, the radial foil bearing therefore has two foils in contact with each other and an outer ring carrying the foils, whereby the radial foil bearing can be accommodated in a housing. The outer ring can also be formed in one piece with the housing into which the foils of the radial foil bearing are inserted.
If the shaft is placed in a rotational movement relative to the radial foil bearing, air present in the air gap defined by the stationary state is squeezed out. Starting from a specific rotational speed of the shaft, an air cushion is formed between the cover foil and the shaft, on which air cushion the shaft can slide. In this case, the foil arrangement, together with its corrugated foil and its radial spring action, ensures that fluctuations in the air pressure or vibrations of the shaft in the radial direction do not damage the bearing, so that the air cushion is maintained in its load-bearing capacity.
Various forms of foil bearings are known in the prior art. In addition to radial foil bearings, axial foil bearings are also available, which can form an axial load-bearing capacity. The arrangement of the foils of the bearing and their geometrical construction is varied and adapted to each application.
EP 2 942 A1 shows a radial foil bearing with three corrugated foils and an approximately encircling cover foil, wherein the corrugated foils each hook with their hook-shaped ends into their own slits in the outer ring and the cover foil is inserted with its two ends against each other into one of the slits.
EP 3 387,275 A1 shows a radial foil bearing with three groups of cover foil and corrugated foil, wherein each group is inserted into a slit of the outer ring at each end of the foil.
CN 209,990,776u shows a radial foil bearing, in which not only the corrugated foil but also the cover foil is formed approximately completely around, each having a bent end, by means of which both foils are inserted into a common slit. The connection is then clamped by means of screws.
It is problematic to arrange the foils economically to optimize the well-functioning load carrying capacity.
Disclosure of Invention
The object of the present invention is therefore to create a radial foil bearing which allows an economical arrangement of the foils and improves the functioning of the radial foil bearing.
The object is achieved by the features of claim 1.
The solution according to the invention comprises a radial foil bearing with an integrated fixed stop as overload protection and shaft displacement limiting mechanism, against which stop the shaft to be carried can hit so that the radial foil bearing is protected from failure or damage. Furthermore, the compressor in which the radial foil bearing according to the invention is used is also protected from failure by the solution according to the invention, wherein the free passage between the compressor wheel and the housing wall surrounding it is maintained.
The invention therefore proposes a radial foil bearing having an outer ring, a corrugated foil and a cover foil, wherein the corrugated foil is arranged radially between the outer ring and the cover foil and forms at least three foil groups of exactly one corrugated foil and exactly one cover foil, which are arranged on the inner circumferential surface of the outer ring and follow one another along the inner circumferential surface, wherein for each foil group a radially inwardly directed stop for the shaft to be supported is provided, which stop is formed by the inner circumferential surface of the outer ring, wherein a first radial gap between the stop and the shaft to be supported opposite the stop is smaller than a second radial gap between a component connected rotationally fixed to the shaft to be supported and a housing wall opposite the component.
By means of the solution according to the invention, the component stresses which are not reliably high when the corrugated foil is compressed too high are reduced and fracture of the corrugated foil or plastic deformation of the spring structure of the corrugated foil is avoided. By limiting the radial shaft displacement and thus the spring path according to the invention, damage to the compressor wheel in the radial foil bearing or connected to the shaft to be carried can be prevented.
The technical design of the corrugated spring foil, which meets the requirements regarding foil bearing function and impact load absorption, is significantly simplified by the solution according to the invention. The radial spring constant of the corrugated foil can now be selected to absorb the impact load in a matched manner, so that the force of the air pressure built up by the rotation of the shaft in the bearing gap is sufficient to form a large-area and load-bearing support surface with a constant bearing gap between the cover foil and the rotary shaft.
The dimensioning of the first radial gap with respect to the stop increases the efficiency of the compressor, since it limits the displacement of the compressor wheel by the second radial gap and determines the second radial gap together with respect to its order of magnitude. The smaller the gap, the higher the efficiency of the compressor. Thus, the definition of the maximum reliable radial shaft displacement prevents solid contact between the compressor wheel and the surrounding compressor housing.
By the present invention a radial foil bearing is proposed which allows optimizing the support structure constituted by the lid foil and the corrugated foil while limiting radial compression without exceeding the allowable material stress of the corrugated foil.
In order to avoid damage to the contact partners, which are formed by the cover foil and the shaft to be carried, in the case of solid contact, at least one or both of the contact partners is provided with a friction-reducing and/or wear-preventing coating.
The radial foil bearing has a foil set consisting of at least one cover foil and at least one corrugated foil, but preferably of exactly one cover foil and exactly one corrugated foil, wherein the foil set has a resilient steel plate foil structure which, in operation, permits a radial displacement of the shaft relative to the housing to a certain extent. The shaft displacement occurring during operation is in this case essentially dependent on the stiffness of the bearing and the occurring static and dynamic forces. The flexibility of the foil bearing is a defined property in this case, so that a stable operation can be achieved by the air cushion built up in the contact between the shaft and the bearing during rapid rotation of the shaft, which generates a large-area and thus load-bearing support surface. However, the radial displacement of the shaft is not allowed to exceed a certain limit value, since otherwise undesired solid contact (e.g. contact of the compressor wheel with the housing) can occur between the rotating and stationary components of the compressor. In particular, impact loads introduced from the outside into the vehicle during operation can generate high forces and cause correspondingly large radial deflections of the shaft.
Preferably, the greatest elastic radial compression of the foil assembly is limited by a plurality of stops in the bearing. If the shaft to be carried is subjected to a radial displacement beside one stop, the shaft to be carried is radially restrained at both stops, between which the shaft to be carried is allowed to compress the foil set to an allowed value. Between the two stops, the radial displacement reaches its maximum value just centrally between the two stops following each other in the circumferential direction. When the shaft to be supported just hits a stop, a minimum radial displacement of the shaft to be supported is achieved.
Advantageously, a fastening surface for the foil set or one of the foils of the foil set is formed by the stop radially in the direction of the shaft to be carried and protruding from the inner side of the outer ring. In other words, the fixing surface for the foil set or one of the foils of the foil set, which faces radially in the direction of the shaft to be carried and protrudes from the inner side of the outer ring, acts as a stop for limiting the radial displacement of the shaft to be carried.
The one or more stops are configured such that they have a stiffness at least three times higher than the foil set.
In an advantageous embodiment of the invention, each foil group is fixedly connected to one another at one end and at the same time to the outer ring in the region of the stop with the outer ring, wherein the other ends of the foil groups contact one another and the outer ring, so that a relative movement of the foils with respect to one another and with respect to the outer ring is possible.
A preferred embodiment provides that the foil groups formed by the cover foil and the corrugated foil lie flat against one another in the region of the stop, so that the jointly formed end faces point in the circumferential direction and the contact faces between one another are formed by sections of the circumferential surface.
In one embodiment of the invention, the stop of the outer ring has an extension in the axial direction, which corresponds to the axial extension of the foil arrangement for the abutment surface of the end face of the stop.
In one embodiment, the cover foil covers the stop at least partially and a radial gap is formed between the shaft to be supported and the cover foil.
Advantageously, the stop is formed so as to be radially offset relative to the envelope circle in the bearing bore, i.e. the radial distance from the center of the envelope circle to the side of the envelope circle (envelope circle radius) is smaller than the radial distance from the center of the envelope circle to the stop. The term bearing bore is understood here to mean a bore concentric with the bearing center without components, into which bore the shaft to be carried is inserted. Alternatively, the stop protrudes in the radial direction inwards in the radial direction from the envelope circle of at least one of the cover foils. The envelope circle of the arcuate cover foil is formed by its radius and defines an interior space free of components except for the shaft to be carried.
According to an advantageous embodiment, the stop has a stop edge for peripherally stopping at least one foil of the foil set.
The radial foil bearing arrangement according to the invention with a radial foil bearing also achieves the object in that the compressor wheel is connected in a rotationally fixed manner to the shaft to be carried by the radial foil bearing, said compressor wheel having a second radial play with respect to its housing wall. The radial gap between the compressor wheel and its surrounding housing wall is greater than the radial gap between the shaft to be carried and the stop of the radial foil bearing, whereby in vibrations causing a radial displacement of the shaft in the radial foil bearing, the shaft to be carried can hit the stop or stops in the radial foil bearing and thereby also limit the radial displacement of the compressor wheel, whereby the compressor wheel has a sufficient radial distance from its housing wall and does not contact said housing wall.
The shaft and/or the stop to be carried may be provided with a friction and wear reducing coating.
A stop at the inner ring circumference in the outer ring of the radial foil bearing can be used for accurate positioning of the foil at the outer ring. In this case, the group of one cover foil and one corrugated foil is positioned at the end side in each case at the same time at the single stop or at the radially extending step of the stop edge. Thus, the foils are precisely positioned relative to each other and relative to the outer ring.
The "outer ring" in the context of the invention can be inserted into the housing as a separate component, as an "outer component", or can be formed in one piece with the housing, the outer ring formed integrally with the housing being present as a housing bore, the stop being formed integrally by a wall of the housing bore. In the context of the present invention, the multi-part design ("outer part") and the one-part design ("housing bore") are collectively referred to as the "outer ring". It is important for the invention of the radial foil bearing that the foil groups can be placed in the ring shape of the outer ring.
One or more stops, which are formed in one piece from the outer ring of the radial foil bearing, are radially inwardly recessed from the inner circumferential surface for abutment against the foil assembly. In other words, the stopper protrudes radially inward from the inner circumferential surface. The one or more stops are preferably formed in a platform-like manner, which is in planar contact or can be in contact with the foil of the foil set or the foils of the foil set. The shaft to be carried can be in direct contact with the stop or indirectly via a member arranged between them, for example a foil of a foil set.
Preferably, the cover foil and the corrugated foil lie flat against one another in the region of the stop, so that the end-side faces of the two foils point in the circumferential direction and the contact faces with one another are formed by sections of the circumferential surface of the foils. The corrugated foil has no curled profile in said region. The circumferential surface follows as much as possible the shape of a circular arc and thus the geometry of the inner side of the outer ring.
The end faces of the two foils of the foil arrangement can jointly rest on a radial step, wherein alternatively it is also possible for one of the foils of the foil arrangement to rest on the step by means of its end face, wherein the other foil is spaced apart from the step. In both cases, the foil groups are reliably and correctly positioned in the circumferential direction relative to the outer ring via the steps.
If both foils should be in contact with the steps simultaneously by means of their respective end-side faces, the steps for each foil can have a geometry as initially mentioned which is different from each other, as long as the contact between each foil and each step blocks the degree of freedom (in circumferential direction). As an example, a stair-like, recessed embodiment of the steps is conceivable here, wherein each foil is in contact with its step by means of its contact surface on the end face.
The radial foil bearing, which advantageously has three foil groups arranged circumferentially behind one another, enables only one rotational direction of the shaft to be supported and thus a unidirectional formation. In particular, it is not possible to operate and the direction of rotation of the counter shaft is not set aside. The radial foil bearing according to the invention enables only one shaft rotational direction by its construction. The directional configuration of the radial foil bearing is thereby necessary, whereby the rotational direction of the shaft to be carried corresponds to the running rotational direction of the radial foil bearing. For this purpose, a plurality of stops according to the invention or a stop according to the invention is used as the orientation means.
In a preferred embodiment of the invention, the axial extension of the inner circumferential surface of the outer ring corresponds to the width of the corrugated foil or the cover foil or the foil set, in order to ensure a reliable support in the circumferential direction.
The fixed connection of the foil groups to the outer ring is preferably provided at one end of the foil or foils, which end is in the region of the stop. The other end of the foil or foils is/are thus formed loose from the outer ring, however, in abutment with each other and with the outer ring. The fixed connection of the foil arrangement to the outer ring and/or to the foil can preferably be performed by laser welding or resistance spot welding.
It can advantageously be provided that the cover foil of one foil set overlaps with the cover foil of the foil set following this in the circumferential direction with a radial distance. As a result, the circumferential support surface is advantageously increased and the installation space between the individual foil groups in the circumferential direction is also significantly better utilized for this purpose. The radial distance is defined here such that the geometry of the cover foil changes in the circumferential direction. In the region of the stop, the cover foil is on a different pitch circle than outside the stop. The free ends of the cover foils of one foil set can thus overlap the fixed ends of the cover foils of the foil set following this on the circumferential side, with radial spacing and without touching each other.
It can also be provided that the free end of the cover foil of one foil set overlaps the fixed end of the cover foil of the foil set following this on the circumferential side so as to form a face of the stop.
The circumferential distance between two following cover foils is dimensioned such that they do not touch one another during operation, in particular when the radial foil bearing or the shaft is vibrating. However, the distance on the circumferential side is also designed such that tearing of the air cushion is avoided, for example, the distance is measured as a function of the eddy currents occurring at the ends of the foil.
According to the invention, it is to be avoided that the elongation of the corrugated foil during operation or the overlapping of the cover foils causes contact of the stop.
Drawings
Embodiments of the present invention are described in detail in the following figures.
The drawings show:
figure 1 shows a radial foil bearing without overload protection and travel limiting mechanism for a shaft to be carried,
figure 2 shows the radial foil bearing according to figure 1 in the case of a radial displacement of the shaft to be carried,
figure 3 shows a first embodiment according to the invention of a radial foil bearing with a stop without radial displacement of the shaft to be carried,
figure 4 shows the radial foil bearing according to figure 3 in the case of a radial displacement of the shaft to be carried,
fig. 5 shows a radial foil bearing according to a second embodiment of the invention with a stop in the case of a radial displacement of the shaft to be carried, and
fig. 6 shows a third embodiment of a radial foil bearing according to the invention with a stop in the case of a radial displacement of the shaft to be carried.
Detailed Description
Fig. 1 shows a radial foil bearing 1 for a shaft 7 to be supported without overload protection and travel limiting means. The shaft 7 rotating in the direction of rotation 14 is in the center of the radial foil bearing 1, because the shaft 7 is carried by an air cushion formed between the outer circumferential surface of the shaft 7 and the cover foil 4.
Fig. 1 shows a radial foil bearing 1 with an outer ring 2, a corrugated foil 3 and a cover foil 4, wherein the corrugated foil 3 and the cover foil 4 form a foil set 8. The three foil groups 8 are arranged in a pattern following one another on the circumference of the outer ring 2 and at regular intervals from one another. In this case, the corrugated foil 3, which has a wave form when viewed in the circumferential direction of the foil bearing 1, rests against the inner circumferential surface 5 of the outer ring 2. On the side of the corrugated foil 3 opposite the outer ring 2, the cover foil 4 rests against the corrugated foil 3. The wave form of the corrugated foil 3 is capable of compressing the cover foil 4 towards the outer ring 2.
Between the outer circumferential surface of the shaft 7 and each cover foil 4, the gap, which remains as constant as possible on the circumferential side during operation and during normal operation, is formed along the circumferential direction 11 by an air cushion which is carried.
Fig. 2 shows the radial foil bearing 1 according to fig. 1 in the case of a radial displacement of the shaft 7 to be carried. The displacement of the shaft 7 in the displacement direction 15 can take place by static (e.g. the weight of the shaft 7) and dynamic loading during operation of the radial foil bearing 1. The load acts on the air cushion and the foil set are compressible. If the displacement caused by the compression is too great, the radial foil bearing 1 may damage and/or contact components connected in a rotationally fixed manner to the shaft 7, for example, a compressor wheel, which is not shown here, with its peripheral components, for example, a housing wall surrounding the compressor wheel. The radial distance on the opposite side of the shaft 7 from the contact of the cover foil 4 increases and reaches an unreliable high value without the stop 6.
Fig. 3 shows a first embodiment of the radial foil bearing 1 according to the invention with a stop 6 as overload protection or shaft displacement limiting means without showing the radial displacement of the shaft 7 to be carried. The shaft 7 rotates in the direction of rotation 14, whereby an air cushion is formed between the outer circumferential surface of the shaft 7 and the cover foil 4 and carries the shaft 7 at a distance from the cover foil 4. The radial foil bearing 1 is in a safe operating state. The stop 6 protruding radially inwards from the inner circumferential surface 5 of the outer ring 2 now defines a gap 9 with the outer circumferential surface of the shaft 7, which gap is smaller than the radial gap of the compressor wheel connected to the shaft 7 in a rotationally fixed manner with respect to its circumferential housing wall, which surrounds the compressor wheel.
The stop 6 protrudes in a flat manner from the inner circumferential surface 5 and forms both an axial displacement limiting means for the shaft 7 and a fastening surface for a foil set 8, which is formed by exactly one lid foil 4 and exactly one corrugated foil 3. The foils 3 and 4 rest against each other by means of the abutment surface 12 and also against the stop 6. The contact of the foil assembly 8 with the stepped stop edge 10 is limited in the circumferential direction 11 by its contact surface 13 on the end face. The stop edges 10 rest against the stop 6 following one another in the circumferential direction 11. Following the stop edge 10 in the direction of rotation 14 of the shaft 7 is the stop 6 and then a radially elastic region of the foil arrangement 8, which is fixedly connected to the preceding stop 6.
Fig. 4 shows the radial foil bearing 1 according to fig. 3 in the case of a radial displacement of the shaft 7 to be carried. When a radial force component is applied that interferes with a reliable operating state, the shaft 7 is displaced eccentrically to its initial axis of rotation and indirectly comes to rest against a stop 6, which thereby limits the further displacement of the shaft 7. The indirect contact with the stop 6 is based on the fact that, in this embodiment of the invention, the foils 3 and 4 of the foil arrangement 8, which are fixedly connected to the stop 6, are arranged between the outer circumferential surface of the shaft 7 and the stop 6. However, the thickness of the foil is negligible in the stopping behavior. The foils 3 and 4 of the foil arrangement 8 rest with their circumferential contact surfaces 12 against one another and also in this region against the platform-like stop 6. The contact surface 13 on the end face contacts a stepped stop edge 10 which, when mounted on the outer ring 2, delimits and positions the foils 3,4 in the circumferential direction 11.
Fig. 5 shows a second embodiment of the radial foil bearing 1 according to the invention with a stop 6 in the case of a radial displacement of the shaft 7 to be carried. In this embodiment, the stop edge 10 is not formed as a step. More precisely, the normal vector of the contact surface 13 is formed in the circumferential direction parallel to the limiting surface of the stop 6, which limiting surface is moved radially inward from the outer ring 2 by a plateau-like design. On the side face (limiting face) of the limiting stop 6, the abutment face 13 is oriented flush as shown. Whereby more structural space in the circumferential direction 11 can be obtained, for example to increase the carrying length of the circumferential side of the cover foil 4, or to reduce the radial or diametrical extension of the radial foil bearing 1.
Fig. 6 shows a third embodiment of the radial foil bearing 1 according to the invention with a stop 6 in the case of a radial displacement of the shaft 7 to be carried. The stop 6 is compressible as a spring element 16 itself as shown here and not only limits the displacement of the shaft 7, but also brakes its movement in order to reduce the force impact when it comes into contact with the stop 6 (indirectly or directly). The spring element 16 is formed as a separate component from the outer ring 2 and is inserted into a receptacle at the inner circumferential surface 5 of the outer ring 2. The spring element 16 can also be used as a receptacle for securing the foil ends of the foils 3 and 4 of the foil set 8.
Description of the reference numerals
1. Radial foil bearing
2. Outer ring
3. Corrugated foil
4. Cover foil
5. An inner circumferential surface
6. Stop block
7. Shaft to be carried
8. Foil set
9. Gap of
10. Stop edge
11. Circumferential direction
12. Surface for sticking
13 leaning surface (end side)
14 direction of rotation
15 Direction of displacement (of shaft)
16 spring elements.

Claims (9)

1. A radial foil bearing (1) having:
-an outer ring (2), a corrugated foil (3) and a lid foil (4), wherein
-the corrugated foil (3) is radially arranged between the outer ring (2) and the cover foil (4), and
forming at least three foil sets (8) of at least one corrugated foil (3) and at least one cover foil (4), which are arranged at and following each other along the inner circumferential surface (5) of the outer ring (2),
it is characterized in that the method comprises the steps of,
for each foil group (8), a radially inwardly directed stop (6) for the shaft (7) to be supported is provided, which is formed by the inner circumferential surface (5) of the outer ring (2), wherein a first radial gap (9) between the stop (6) and the shaft (7) to be supported opposite thereto is smaller than a second radial gap between a component connected in a rotationally fixed manner to the shaft (7) to be supported and a housing wall opposite thereto.
2. Radial foil bearing (1) according to claim 1,
it is characterized in that the method comprises the steps of,
each foil set (8) is fixedly connected to each other at one end and simultaneously to the outer ring (2) in the region of the stop (6) with the outer ring (2), wherein the other ends of the foil sets (8) are in contact with each other and the outer ring (2) such that a relative movement of the foils (3, 4) with respect to each other and with respect to the outer ring (2) is possible.
3. Radial foil bearing (1) according to any one of the preceding claims,
it is characterized in that the method comprises the steps of,
the foil groups (8) consisting of the cover foil (4) and the corrugated foil (3) rest against one another in a planar manner in the region of the stop (6) in such a way that the jointly formed end faces point in the circumferential direction (11) and the rest surfaces (12) against one another are formed by sections of the circumferential surface.
4. Radial foil bearing (1) according to any one of the preceding claims,
it is characterized in that the method comprises the steps of,
the stop (6) of the outer ring (2) has an extension in the axial direction, which corresponds to the axial extension of the foil assembly (8) for the abutment surface (13) of the end face of the stop (6).
5. Radial foil bearing (1) according to any one of the preceding claims,
it is characterized in that the method comprises the steps of,
the cover foil (4) at least partially covers the stop (6) and a radial gap (9) is formed between the shaft (7) to be carried and the cover foil (4).
6. Radial foil bearing (1) according to any one of the preceding claims,
it is characterized in that the method comprises the steps of,
the stop (6) has a distance from the bearing center in the radial direction which is greater than the magnitude of the envelope circle radius of the bearing bore without the component.
7. Radial foil bearing (1) according to any one of the preceding claims,
it is characterized in that the method comprises the steps of,
the stop (6) has a stop edge (10) for stopping at least one foil (3, 4) of the foil arrangement (8) on the circumferential side.
8. A radial foil bearing arrangement having a radial foil bearing (1) according to any one of the preceding claims,
it is characterized in that the method comprises the steps of,
the compressor wheel is connected as a component to a shaft (7) to be carried by the radial foil bearing (1) in a rotationally fixed manner, said compressor wheel having a second radial play from its housing wall.
9. A compressor having a radial foil bearing arrangement according to claim 8, wherein the housing wall is a housing wall radially opposite and surrounding a compressor wheel.
CN202280027282.7A 2021-04-09 2022-03-29 Radial foil bearing with overload protection and shaft displacement limiting mechanism Pending CN117222819A (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102021108888.7 2021-04-09
DE102021108888.7A DE102021108888A1 (en) 2021-04-09 2021-04-09 Radial foil bearing with overload protection and shaft displacement limitation
PCT/DE2022/100243 WO2022214133A1 (en) 2021-04-09 2022-03-29 Radial foil bearing having an overload protection and a shaft displacement limiting mechanism

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US6698930B2 (en) 2000-12-01 2004-03-02 Mitsubishi Heavy Industries, Ltd. Foil gas bearing
US7614792B2 (en) 2007-04-26 2009-11-10 Capstone Turbine Corporation Compliant foil fluid film radial bearing or seal
JP2013032797A (en) * 2011-08-01 2013-02-14 Ntn Corp Foil bearing
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DE102015224869A1 (en) 2015-12-10 2017-06-14 Schaeffler Technologies AG & Co. KG foil bearings
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CN209990776U (en) 2019-05-13 2020-01-24 大连理工大学 Cuboid pin type air dynamic pressure foil bearing foil fixing structure

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