Self-aligning bearing support and centrifugal compressor

Abstract

The utility model belongs to the technical field of centrifugal machines, and discloses a self-aligning bearing support and a centrifugal compressor, the self-aligning bearing support comprises a bearing shell, a bearing support and a flexible supporting support, the bearing shell is provided with a first mounting hole, the bearing support is mounted in the first mounting hole, and the bearing support is provided with a second mounting hole for inserting a bearing; the flexible supporting support comprises an elastic piece and a damping piece, the elastic piece is arranged around the bearing support and clamped between the bearing support and the bearing shell, the damping piece is arranged on the elastic piece in a surrounding mode, and at least the elastic piece can deform so as to be installed to adjust the coaxiality of a shaft system of the bearing. The centrifugal compressor comprises a shaft system, a bearing and two self-aligning bearing supports in any form, the bearing is arranged in the second mounting hole of the bearing support, the shaft system is mounted on the bearing, and therefore automatic aligning can be achieved, vibration and noise reduction is achieved, and the service life is prolonged.

Description

TECHNICAL FIELD

[0001] The utility model relates to centrifuge technical field especially, it relates to a self-aligning bearing support and centrifugal compressor. BACKGROUND

[0002] Rotor dynamics is very important for high-speed centrifugal machinery, rotor dynamics mainly studies including two end impeller, bearing assembly, motor rotor and shaft of the whole shafting: undamped critical speed, damped critical speed, bearing stiffness matrix and damping matrix, damped shafting unbalance response, mode shape of the shafting under each critical speed, whether the maximum unbalance response value of bearing node under each critical speed exceeds bearing clearance, whether the maximum unbalance response value of motor shaft center node under each critical speed exceeds stator-rotor air gap, whether the maximum unbalance effect value of two end impeller node under each critical speed exceeds impeller maximum clearance, etc. Figure 15 The critical speed curve of rotor system under different bearing stiffness is given. The first order, second order and third order critical speed corresponding to the stiffness of bearing are obtained. If the design speed is less than the critical speed, the compressor is stable when running at the design speed. If Figure 16 The unbalance response value of shaft center position is obtained.

[0003] Evaluation standard one of rotor dynamics analysis: the working speed of compressor shafting is less than the first order critical speed of rotor, and the first order critical speed is required to be greater than 1.2-1.25 times of the highest working speed. The influence of damping needs to be considered, and the avoidance margin of rotor is evaluated by different amplification coefficients.

[0004] Evaluation standard two: the maximum response value of each part under different speed is given for the response of rotor. The maximum unbalance response value is required to be less than 0.75 times of the matching clearance to meet the actual engineering requirements.

[0005] The traditional centrifugal compressor design is to fix the bearing support in the inner shell of the compressor bearing seat shell through rigid connecting bolts or flange plates, and the shafting of the bearing support is installed and fixed in the hole inner diameter of the bearing seat shell. In this way, the bearing, bearing support and bearing seat shell are rigidly connected. Since the two ends of the motor rotor are respectively arranged with two bearing supports and bearing seat shells to realize effective bearing installation and fixation, the above traditional method has the following problems: one is that the machining precision of the rotary circular surface is very high, such as Figure 17As shown, the center of the hole inner diameter φD1 of the bearing seat shell for sleeving the bearing support, the center of the shaft outer diameter φd1 of the bearing support, the center of the bearing outer ring diameter φd2 and the center of the bearing mounting hole inner diameter φD2 of the bearing support. Similarly, the cumulative value of the coaxiality between the other end bearing assembly φd1", φD1", φd2", φD2", a total of 8 machined centers, generally requires 2 silk ~ 4 silk (0.02mm ~ 0.04mm), which requires very high machining accuracy of each part, otherwise it is easy to appear because of the axis (connecting shaft) two end different shaft, resulting in rotation is limited, the extreme case may cause the axis to be stuck; secondly: the requirement of assembly and maintenance is higher, in the process of assembly and disassembly, the tight fit design between the parts will make the assembly and installation of the parts become difficult; thirdly: Figure 16 As shown, due to vibration during rotation, each part of the shaft system will generate unbalanced response value due to dynamic imbalance, and additional dynamic load radial force will be generated, which will gradually increase with the increase of rotating speed, thereby affecting the operation reliability and service life of the bearing itself; fourthly: because the whole shaft system is rigidly connected, during the rotation of the compressor and the process of driving rotation by the motor torque, the motor stator will heat up, the motor rotor will be heated by the motor stator, and the centrifugal expansion of the motor rotor itself will cause additional bearing static load radial force, which will affect the operation reliability and service life of the bearing itself with the increase of temperature.

[0006] All the above static load and dynamic load will increase the additional stress on the bearing, and the dynamic imbalance of the rigidly connected shaft system will be transmitted through vibration from the bearing, to the bearing support, to the bearing seat shell, and to the whole compressor shell, and finally transmitted to the steel beam of the unit through the compressor base, and then the vibration is fed back to the bearing seat through the rigidity, the vibration and noise of the whole shaft system will be improved, and the service life of the bearing will be reduced. Practical new type content

[0007] The purpose of the present application is to provide a self-aligning bearing support and a centrifugal compressor, which can automatically align, realize vibration and noise reduction, and improve the service life of the bearing.

[0008] To achieve this purpose, the present application adopts the following technical solutions:

[0009] The self-aligning bearing support comprises:

[0010] A bearing shell, the bearing shell is provided with a first mounting hole;

[0011] A bearing support is installed in the first mounting hole, and the bearing support is provided with a second mounting hole for inserting the bearing;

[0012] The flexible support support includes an elastic member and a damping member, the elastic member is arranged around the bearing support and clamped between the bearing support and the bearing housing, and the damping member is arranged around the elastic member to support the elastic member. At least the elastic member can be deformed to adjust the coaxiality of the shaft system installed on the bearing.

[0013] In some embodiments, the damping member is clamped between the elastic member and the bearing support.

[0014] In some embodiments, a side of the damping member facing the bearing support is circumferentially spaced with a plurality of embedding grooves, and a plurality of the elastic members are embedded in the embedding grooves one by one.

[0015] In some embodiments, the damping member includes a ring body surrounding the bearing support, and an inner ring surface of the ring body is circumferentially spaced with a plurality of protrusions, and the embedding grooves are formed between adjacent protrusions.

[0016] In some embodiments, the damping member includes a plurality of fixing bodies circumferentially spaced along the bearing support, and a side of the fixing body facing the bearing support is provided with the embedding grooves, and the elastic member is embedded in the embedding grooves, and the fixing body is provided with a plurality of circumferential cutting grooves along the bearing support, so that the fixing body can be deformed in the radial direction.

[0017] In some embodiments, the damping member is arranged in the elastic member.

[0018] In some embodiments, the damping member and the elastic member are both annular, the damping member is arranged in the elastic member and surrounds the bearing support, and an inner ring surface and an outer ring surface of the elastic member are both circumferentially spaced with a plurality of protruding ribs, and the protruding ribs are located on both sides of the damping member.

[0019] In some embodiments, the elastic member is annular, an inner ring surface of the elastic member is provided with a plurality of groups of protruding ribs, a plurality of groups of the protruding ribs are circumferentially spaced along the inner ring surface of the elastic member, each group of the protruding ribs contains a plurality of protruding ribs, and the damping member is located in the protruding ribs and protrudes to one side of the bearing support in an arc shape.

[0020] In some embodiments, the elastic member is made of non-metallic polymer material, and / or the damping member is made of metallic elastic material.

[0021] A centrifugal compressor is also provided, which includes a shaft system, a bearing, and two self-aligning bearing supports described above, the bearing is arranged in the second mounting hole, and the shaft system is installed on the bearing.

[0022] The utility model discloses the beneficial effect of:

[0023] Elastic member surrounds bearing support arrangement, can extrude elastic member to install when installing, make installation more simple, when the misalignment (off -center) amount of shafting two ends, shafting drives bearing extrusion elastic member, thereby make elastic member produce radial deformation amount and eliminate the off -center degree of shafting, realize automatic alignment, avoid shafting jamming, and make the shafting after alignment be in light load and stable operation, and the friction and friction resistance loss of bearing reduce, effectively eliminate noise, and elastic member has the dissipation effect to vibration, can reduce the kinetic energy of vibration body, help vibration value gradually weaken, make vibration not amplify and return, reach the purpose of vibration and noise reduction, and the reduction of vibration is to the stable operation of shafting, reduce the influence of bearing dynamic load to bearing life. BRIEF DESCRIPTION OF DRAWINGS

[0024] Figure 1 It is the section view of the self-aligning bearing support in the utility model for use;

[0025] Figure 2 It is the section view of the protruding large diameter section connecting ring body in the utility model;

[0026] Figure 3 It is Figure 2 the enlarged view of A in the utility model;

[0027] Figure 4 It is the section view of the protruding small diameter section connecting ring body in the utility model;

[0028] Figure 5 It is Figure 4 the enlarged view of B in the utility model;

[0029] Figure 6 It is the section view of the first form of cutting groove in the utility model;

[0030] Figure 7 It is the second form of cutting groove in the utility model Solid drawing;

[0031] Figure 8 It is the section view of the second form of cutting groove in the utility model;

[0032] Figure 9 It is the section view of the third form of cutting groove in the utility model;

[0033] Figure 10 It is the section view of the fourth form of cutting groove in the utility model;

[0034] Figure 11 It is the opposite section view of the convex rib in the utility model;

[0035] Figure 12is a cross-sectional view of the staggered ribs in the utility model

[0036] Figure 13 is a cross-sectional view of one of the rib groups in the utility model

[0037] Figure 14 is a simulation cross-sectional view of the self-aligning bearing support in the utility model

[0038] Figure 15 is a schematic diagram of the critical speed curve of a rotor system in the prior art under different bearing stiffness

[0039] Figure 16 is a schematic diagram of the unbalance response value of the shafting center position in the prior art

[0040] Figure 17 is a schematic diagram of the coaxiality size of the shafting in the prior art

[0041] Figure 18 is a schematic diagram of the stiffness coefficient and the damping coefficient

[0042] In the drawings:

[0043] 1, bearing shell

[0044] 2, bearing support

[0045] 3, flexible support support; 31, elastic member; 311, rib; 32, damping member; 321, ring body; 322, protrusion; 323, fixed body; 33, gap; 34, cutting groove

[0046] 4, bearing DETAILED DESCRIPTION

[0047] The utility model will be further described in detail below in combination with the drawings and examples. It can be understood that the specific examples described herein are only used to explain the utility model, and not to limit the utility model. In addition, it should be noted that, in order to facilitate the description, only the part related to the utility model is shown in the drawings, not all structures.

[0048] In the description of the utility model, unless otherwise explicitly specified and limited, the terms "connected", "connected", "fixed" should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or it can be integrated, it can be mechanically connected, or it can be electrically connected, it can be directly connected, or it can be indirectly connected through an intermediate medium, it can be the internal communication of two elements or the interaction relationship of two elements. For ordinary skilled in the art, the specific meaning of the above terms in the utility model can be understood according to the specific circumstances.

[0049] In the present application, unless otherwise explicitly specified and limited, the first feature is "on" or "under" the second feature, which can include direct contact between the first and second features, or indirect contact between the first and second features through another feature therebetween.

[0050] In the description of the present application, the terms "up", "down", "left", "right", and other orientation or position relationships are based on the orientation or position relationships shown in the drawings, and are only for the convenience of description and simplification of operation, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the present application. In addition, the terms "first" and "second" are only used to distinguish in the description, and have no special meaning.

[0051] As shown in Figures 1 to 13 The present application provides a self-aligning bearing support, which comprises a bearing shell 1, a bearing support 2 and a flexible support support 3, the bearing shell 1 is provided with a first mounting hole, the bearing support 2 is installed in the first mounting hole, and the bearing support 2 is provided with a second mounting hole for inserting the bearing 4; the flexible support support 3 comprises an elastic member 31 and a damping member 32, the elastic member 31 is arranged around the bearing support 2 and clamped between the bearing support 2 and the bearing shell 1, and the damping member 32 is arranged around the elastic member 31; at least the elastic member 31 can be deformed to adjust the coaxiality of the shafting installed on the adjusting bearing 4.

[0052] The elastic member 31 is arranged around the bearing support 2 and can be squeezed during installation to make the installation more simple; when the shafting at both ends produces a misalignment (different shafting) amount, the shafting drives the bearing to squeeze the elastic member 31, so that the elastic member 31 produces a radial deformation amount to eliminate the different shafting of the shafting, realize automatic alignment, and avoid shafting jamming; and the shafting after alignment is in light load and stable operation, the friction and friction resistance loss of the bearing 4 is reduced, and the noise is effectively eliminated; and the elastic member 31 has a damping effect on vibration, can reduce the kinetic energy of the vibration body, and helps to gradually weaken the vibration value, so that the vibration is not amplified and returned, to achieve the purpose of reducing vibration and noise, and the reduction of vibration helps the stable operation of the shafting and reduces the influence of bearing dynamic load on the service life of the bearing 4.

[0053] In addition, the flexible support support 3 not only provides damping deformation, but also provides sufficient bearing support stiffness N / mm for shafting support to meet Figure 15The intersection point of the support stiffness N / mm curve (usually refers to the bearing stiffness curve in XX direction and the bearing stiffness curve in YY direction) of the bearing and the natural frequency curve of the shafting is greater than the maximum operating speed of the shafting; to meet Figure 16 The maximum response value of each part at different rotating speeds is required to be less than 0.75 times the matching clearance.

[0054] It should be noted that the stiffness coefficient is the resistance to load deformation, the increase in liquid film force caused by unit displacement, which is calculated as follows:

[0055] Formula one,

[0056] Formula two,

[0057] Formula three,

[0058] Formula four,

[0059] The above formula one is the displacement of the liquid film in the X direction caused by the X direction component of the loading force; formula two is the displacement of the liquid film in the Y direction caused by the Y direction component of the loading force; formula three is the displacement of the liquid film in the Y direction caused by the X direction component of the loading force; formula four is the displacement of the liquid film in the X direction caused by the Y direction component of the loading force;

[0060] Wherein,

[0061] F x_max and F x_min are the maximum and minimum values of the X direction component of the loading force;

[0062] F y_max and F y_min are the maximum and minimum values of the Y direction component of the loading force;

[0063] X max and X min are the maximum and minimum values of the X direction displacement component caused by the loading force.

[0064] Y max and Y min are the maximum and minimum values of the Y direction displacement component caused by the loading force.

[0065] The damping coefficient is the ability to eliminate elastic strain energy, defined as the increase in liquid film force caused by unit velocity, calculated as follows:

[0066]

[0067] The first formula above represents the velocity of the liquid film generated in the X direction by the component of the applied force in the X direction; the second formula represents the velocity of the liquid film generated in the Y direction by the component of the applied force in the Y direction; the third formula represents the velocity of the liquid film generated in the Y direction by the component of the applied force in the X direction; the second formula represents the velocity of the liquid film generated in the X direction by the component of the applied force in the Y direction.

[0068] in,

[0069] and The maximum and minimum values ​​of the velocity in the X direction generated by the applied load force.

[0070] and The maximum and minimum values ​​of the velocity in the Y direction generated by the applied load force.

[0071] The stiffness coefficient matrix is ​​given by the formula:

[0072]

[0073] The damping coefficient matrix is ​​given by the formula:

[0074]

[0075] In rotor dynamics analysis, the matrix of the four stiffness coefficients (K) of the bearing support system is studied. xx K yy K xy K yx ) and the matrix of 4 damping coefficients (C xx C yy C xy C yx xy and yx are the cross stiffness coefficient and cross damping coefficient, respectively. Generally, they are not used in engineering analysis in rotor dynamics analysis; only K is studied. xx K yy Two stiffness coefficients and C xx C yy Two damping coefficients. For example... Figure 18 A schematic diagram showing the stiffness coefficient and damping coefficient;

[0076] Figure 18 middle:

[0077]

[0078] Where, [M]: mass matrix of the shaft system, kg; [C]: damping matrix of the shaft system, N / (m·s); [K]: stiffness matrix of the shaft system, N / m; Ω: angular velocity of the shaft system, rad / s; u: unbalanced response value at the nodal displacement of the shaft system, m; Unbalance response value at shafting node velocity, m / s Unbalance response value at shafting node acceleration, m / s2 2 Unbalance response value at shafting node velocity, m / s[Q]: Unbalance force, N.

[0079] It should be further noted that the noise includes the noise generated by the rolling body friction of the bearing 4, the noise of the airflow flow, and the bearing load after the automatic centering coaxiality is basically the weight of the shafting. The radial load of the bearing 4 is reduced, and the axial force of the bearing 4 layout of the back-to-back structure is basically eliminated. Then the entire shafting will be in a light load and stable operation, the friction force and friction resistance loss between the rolling body and the raceway are reduced, which helps to eliminate mechanical friction noise. Furthermore, the lubricating oil at the bearing 4 can further reduce the friction resistance wheel resistance loss, making the noise reduction more obvious. It should be noted here that the bearing housing 1 and the bearing support 2 are prior art, as long as the bearing housing 1 has a first mounting hole for mounting the bearing support 2, and the bearing support 2 has a second mounting hole for inserting the bearing 4. The self-aligning bearing support in the present application can be applied to ball bearings or sliding bearings.

[0080] As shown in Figures 1 to 10 , the damping member 32 is clamped between the elastic member 31 and the bearing support 2. Specifically, the damping member 32 is axially spaced apart from the bearing support 2 and has a plurality of embedding grooves. The elastic member 31 also has a plurality of embedding grooves, and the plurality of elastic members 31 are embedded one by one in the embedding grooves, so that the elastic member 31 contacts the bearing support 2.

[0081] Among them, the elastic member 31 is made of non-metallic polymer material, such as nylon, PTFE, rubber and other soft non-metallic polymer materials; the damping member 32 is made of metal elastic material, such as steel or steel alloy. The elastic member 31 adopts the above-mentioned non-metallic polymer material, when subjected to alternating stress (or vibration), because the movement of chain-like macromolecules needs time to overcome the frictional resistance between chain segments, therefore, the deformation of the elastic member 31 often lags behind the change of stress. This lag is very obvious at a certain temperature and frequency, and the deformation means energy consumption, which reduces the kinetic energy of the vibration body and achieves the purpose of vibration reduction.

[0082] As shown in Figure 2 and Figure 5As shown, in some embodiments, the damping element 32 includes a ring body 321 surrounding the bearing bracket 2. The ring body 321 can be fixedly connected to the bearing housing 1, including but not limited to welding, snap-fitting, or bolting. The inner ring surface of the ring body 321 is circumferentially spaced with several protrusions 322. Adjacent protrusions 322 form a groove. Each protrusion 322 includes an integrally formed large-diameter section and a small-diameter section, making the protrusion 322 T-shaped, i.e., forming a limiting step on the protrusion 322. In one embodiment, the large-diameter section of the protrusion 322 connects to the ring body 321, and the elastic element 31 is also T-shaped. During installation, the elastic element 31 is inserted into the groove and overlaps the limiting step of two adjacent limiting protrusions 322. In the current structure, to ensure that the elastic element 31 has a large elastic deformation space, there is a gap 33 between the elastic element 31 and the bottom of the groove. The gap 33 can be, but is not limited to, 0.03mm-0.08mm. Figure 4 As shown, in some alternative embodiments, the small-diameter section of the connecting ring body 321 of the protrusion 322, in order to adapt to the above structure, has an corresponding elastic element 31 that is I-shaped, so that the protrusion 322 and the elastic element 31 are interlocked. In the current structure, in order to make the elastic element have a large elastic deformation space, there is a gap 33 between the side of the large-diameter section of the protrusion 322 facing the bearing bracket 2 and the elastic element 31. This gap 33 can also be, but is not limited to, 0.03mm-0.08mm. In addition, there can also be a certain interval space for deformation between the small-diameter section and the elastic element 31, as well as between two adjacent elastic elements 31, without specific limitation.

[0083] like Figures 6 to 10 As shown, in some embodiments, the damping element 32 includes multiple fixed bodies 323 spaced circumferentially along the bearing support 2. The fixed bodies 323 can be fixedly connected to the bearing housing 1, including but not limited to welding, snap-fitting, or bolting. A groove is provided on the side of the fixed body 323 facing the bearing support 2, and the elastic element 31 is embedded in the groove. To ensure the stability of the embedding, the elastic element 31 is I-shaped, and the groove is also I-shaped. A cutting groove 34 is provided on the fixed body 323, the width of which is the same as the radial direction of the bearing support 2. This allows the pressure to be transmitted to the fixed body 323 when the elastic element 31 is compressed by the bearing support 2, causing the fixed body 323 to deform in the width direction of the cutting groove 34. This, in turn, cancels out the different axialities at both ends of the shaft system through the common deformation of the elastic element 31 and the fixed body 323, achieving self-alignment. In the current embodiment, to facilitate the forming of the cutting groove 34, the cutting groove 34 is S-shaped or multi-segmented intermittent arc shape. Figures 5 to 9The slot width of the cutting slot 34 can also be 0.03mm-0.08mm. The elastic effect of the above-mentioned damping member 32 can further help to gradually weaken the vibration value, so that the vibration is not amplified and returned, and the reduction of the vibration value helps to stabilize the operation of the shafting, thereby improving the service life of the bearing 4.

[0084] As shown in the drawings, in some embodiments, the elastic member 31 is arranged between the bearing housing 1 and the bearing support 2, and the damping member 32 is arranged in the elastic member 31 for supporting the elastic member 31. Specifically, as shown in the drawings, in some embodiments, the damping member 32 and the elastic member 31 are annular, and the inner and outer annular surfaces of the elastic member 31 are circumferentially spaced apart by a plurality of ribs 311, which are located on the inner and outer sides of the damping member 32. The protrusions 322 on the inner and outer annular surfaces can be arranged relatively or staggered, without specific limitation. Figures 11 to 13 Figure 10 Figure 11 As shown in the drawings, in some embodiments, the elastic member 31 is arranged between the bearing housing 1 and the bearing support 2, and the damping member 32 is arranged in the elastic member 31 for supporting the elastic member 31. Specifically, as shown in the drawings, in some embodiments, the damping member 32 and the elastic member 31 are annular, and the inner and outer annular surfaces of the elastic member 31 are circumferentially spaced apart by a plurality of ribs 311, which are located on the inner and outer sides of the damping member 32. The protrusions 322 on the inner and outer annular surfaces can be arranged relatively or staggered, without specific limitation. Figure 12 As shown in the drawings, in some embodiments, the elastic member 31 is arranged between the bearing housing 1 and the bearing support 2, and the damping member 32 is arranged in the elastic member 31 for supporting the elastic member 31. Specifically, as shown in the drawings, in some embodiments, the damping member 32 and the elastic member 31 are annular, and the inner and outer annular surfaces of the elastic member 31 are circumferentially spaced apart by a plurality of ribs 311, which are located on the inner and outer sides of the damping member 32. The protrusions 322 on the inner and outer annular surfaces can be arranged relatively or staggered, without specific limitation.

[0085] Figure 14 As shown in the drawings, in some embodiments, the elastic member 31 is arranged between the bearing housing 1 and the bearing support 2, and the damping member 32 is arranged in the elastic member 31 for supporting the elastic member 31. Specifically, as shown in the drawings, in some embodiments, the damping member 32 and the elastic member 31 are annular, and the inner and outer annular surfaces of the elastic member 31 are circumferentially spaced apart by a plurality of ribs 311, which are located on the inner and outer sides of the damping member 32. The protrusions 322 on the inner and outer annular surfaces can be arranged relatively or staggered, without specific limitation.

[0086] ​​​The application further provides a centrifugal compressor, which comprises a shafting, a bearing 4 and two self-aligning bearing supports of any one of the above forms.

[0087] Obviously, the above embodiments of the present application are merely examples for clearly illustrating the present application, and are not intended to limit the implementation modes of the present application. For those skilled in the art, various obvious changes, re-adjustments and substitutions can be made without departing from the protection scope of the present application. Here, it is unnecessary and impossible to enumerate all the implementation modes. Any modification, equivalent substitution and improvement made within the spirit and principle of the present application shall be included in the protection scope of the present application claim.

Claims

1. Self-aligning bearing support, characterized in that, include: The bearing housing (1) is provided with a first mounting hole; The bearing bracket (2) is installed in the first mounting hole and is provided with a second mounting hole for inserting the bearing (4); A flexible support (3) is provided, comprising an elastic element (31) and a damping element (32). The elastic element (31) is arranged around the bearing bracket (2) and clamped between the bearing bracket (2) and the bearing housing (1). The damping element (32) is arranged around the elastic element (31) to support the elastic element (31). At least the elastic element (31) can deform to adjust the coaxiality of the shaft system installed on the bearing (4).

2. The self-aligning bearing mount of claim 1, wherein, The damping element (32) is clamped between the elastic element (31) and the bearing bracket (2).

3. The self-aligning bearing mount of claim 1, wherein, The damping member (32) has a plurality of grooves spaced apart circumferentially on the side facing the bearing bracket (2), and a plurality of elastic members (31) are correspondingly embedded in the grooves.

4. The self-aligning bearing housing according to claim 3, characterized in that The damping element (32) includes a ring body (321) surrounding the bearing bracket (2), and the inner ring surface of the ring body (321) is provided with a plurality of protrusions (322) spaced apart in the circumferential direction, and the groove is formed between adjacent protrusions (322).

5. The self-aligning bearing support of claim 3, wherein, The damping element (32) includes a plurality of fixed bodies (323) spaced apart circumferentially along the bearing bracket (2). The fixed body (323) has a groove on the side facing the bearing bracket (2). The elastic element (31) is embedded in the groove. The fixed body (323) is provided with a cutting groove (34) so ​​that the fixed body (323) can deform in the radial direction.

6. The self-aligning bearing cartridge of claim 1 wherein, The damping element (32) is disposed within the elastic element (31).

7. A self-aligning bearing housing according to claim 6, characterized in that Both the damping element (32) and the elastic element (31) are annular; the inner and outer annular surfaces of the elastic element (31) are provided with a plurality of convex ribs (311) spaced apart in the circumferential direction, and the convex ribs (311) are located on the inner and outer sides of the damping element (32).

8. The self-aligning bearing cartridge of claim 6 wherein, The elastic element (31) is annular, and the inner ring surface of the elastic element (31) is provided with several sets of ribs. The several sets of ribs are arranged circumferentially along the inner ring surface of the elastic element (31). Each set of ribs contains several ribs (311). The several ribs (311) are arranged axially along the elastic element (31). The damping element (32) is located inside the ribs (311) and protrudes into an arc shape towards the bearing bracket (2).

9. Self-aligning bearing seat according to any of claims 1-8, characterized in that The elastic element (31) is made of a non-metallic polymer material; and / or, the damping element (32) is made of a metallic elastic material.

10. A centrifugal compressor characterized by, The centrifugal compressor includes a shaft system, a bearing (4), and two self-aligning bearing supports as described in any one of claims 1-9, wherein the bearing (4) is disposed in the second mounting hole, and the shaft system is mounted on the bearing (4).

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