Self-aligning bearing support and centrifugal compressor

Abstract

The invention 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 invention relates to the technical field of centrifuges, and in particular to a self-aligning bearing support and a centrifugal compressor. Background Art

[0002] Rotor dynamics is very important for high-speed centrifugal machinery. Rotor dynamics mainly studies the entire shaft system including the impellers at both ends, bearing assemblies, motor rotors and shafts: undamped critical speed, damped critical speed, bearing stiffness matrix and damping matrix, damped shaft system unbalanced response, vibration mode of the shaft system at each critical speed, whether the maximum unbalanced response value of the bearing node at each critical speed exceeds the bearing clearance, whether the maximum unbalanced response value of the motor shaft center node at each critical speed exceeds the stator-rotor air gap, whether the maximum unbalanced effect value of the impeller nodes at both ends at each critical speed exceeds the impeller maximum clearance, etc. Fig.15 The critical speed curves of the rotor system under different bearing stiffness are given. The corresponding first-order, second-order and third-order critical speeds are obtained from the stiffness of the bearing. If the design speed is less than the critical speed, the compressor will run stably at this design speed; Fig.16 is the unbalance response value at the center of the shaft;

[0003] The first evaluation criterion for rotor dynamics analysis is that the operating speed of the compressor shaft system is less than the first-order critical speed of the rotor, and the first-order critical speed is required to be greater than 1.2-1.25 times the maximum operating speed; and the influence of damping needs to be considered, and the rotor avoidance margin is evaluated through different amplification factors.

[0004] Evaluation criterion 2: For the rotor response, the maximum response value requirements for each part at different speeds are given. The maximum unbalanced response value is required to be less than 0.75 times the matching clearance to meet the actual needs of the project.

[0005] The traditional centrifugal compressor design is to fix the bearing support to the inner shell of the compressor bearing housing through rigid connecting bolts or flanges, and the shaft system of the bearing support is installed and inserted into the inner diameter of the hole of the bearing housing and fixed. In this way, the bearing, bearing support, and bearing housing are rigidly connected. Since two identical bearing supports and bearing housings are arranged at both ends of the motor rotor to achieve effective bearing installation and fixation; using the above traditional method, first, the machining accuracy requirements for the rotating circular surface are very high, such as Fig.17As shown, the center of the inner diameter φD1 of the hole on the bearing housing for inserting the bearing support, the center of the outer diameter φd1 of the shaft of the bearing support, the center of the outer ring diameter φd2 of the bearing and the center of the inner diameter φD2 of the bearing mounting hole of the bearing support. Similarly, the cumulative value of the coaxiality between the 8 machined center points φd1”, φD1”, φd2”, φD2” of the bearing assembly at the other end generally requires 2 to 4 points (0.02mm to 0.04mm). This requires that the machining accuracy of each part is very high, otherwise the rotation is easily restricted due to the different axes at both ends of the shaft system (connecting shaft), which may cause the shaft system to get stuck in extreme cases; second: the requirements for assembly and maintenance are higher. During the assembly and disassembly process, the tight fit design between the components will make the assembly and installation of the components difficult; third: such as Fig.16 As shown in the figure, due to the vibration during the rotation process, various parts of the shaft system will produce unbalanced response values ​​due to dynamic imbalance, and will generate additional dynamic load radial force. This dynamic load radial force will gradually increase with the increase of rotation speed, thereby affecting the operating reliability and life of the bearing itself; Fourthly: Since the entire shaft system is rigidly connected, during the rotation of the compressor and the rotation of the motor torque, the motor stator will heat up, the motor rotor will be radiated by the heat of the motor stator and the temperature will rise, the centrifugal expansion of the motor rotor itself, etc., will lead to additional static load radial force of the bearing, which will affect the operating reliability and life of the bearing itself as the temperature rises.

[0006] All the increases in static and dynamic loads mentioned above will impose additional forces on the bearings, and the rigid connection will transmit the dynamic imbalance of the shaft system layer by layer through vibration from the bearing, to the bearing bracket, to the bearing seat housing, and to the entire compressor housing. It will eventually be transmitted to the steel beam of the unit through the compressor base, and then the vibration will be fed back to the bearing seat through rigidity. The vibration and noise of the entire shaft system will increase, reducing the service life of the bearings. Summary of the invention

[0007] The object of the present invention is to provide a self-aligning bearing support and a centrifugal compressor, which can automatically align the center, achieve vibration reduction and noise reduction, and increase the service life of the bearing.

[0008] To achieve this object, the present invention adopts the following technical solutions:

[0009] Self-aligning bearing support, comprising:

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

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

[0012] A flexible support seat, the flexible support seat includes an elastic member and a damping member, the elastic member is arranged around the bearing bracket and clamped between the bearing bracket and the bearing housing, 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 bracket.

[0014] In some embodiments, a surface of the damping member facing the bearing bracket is provided with a plurality of embedding grooves at intervals in the circumferential direction, and a plurality of the elastic members are embedded in the embedding grooves in a one-to-one correspondence.

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

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

[0017] In some embodiments, the damping member is disposed within the elastic member.

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

[0019] In some embodiments, the elastic member is annular, and the inner ring surface of the elastic member is provided with a plurality of groups of convex rib groups, and the plurality of groups of convex rib groups are arranged at circumferential intervals along the inner ring surface of the elastic member, and each group of the convex rib groups contains a plurality of convex ribs, and the plurality of convex ribs are arranged at axial intervals along the elastic member, and the damping member is located in the convex ribs and protrudes in an arc shape toward one side of the bearing support.

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

[0021] A centrifugal compressor is also provided. The centrifugal compressor comprises a shaft system, a bearing and two of the above-mentioned self-aligning bearing supports. The bearing is arranged in the second mounting hole, and the shaft system is mounted on the bearing.

[0022] Beneficial effects of the present invention:

[0023] The elastic part is arranged around the bearing bracket, and the elastic part can be squeezed for installation during installation, making the installation easier; when there is misalignment (different axes) at both ends of the shaft system, the shaft system drives the bearing to squeeze the elastic part, so that the elastic part produces radial deformation to eliminate the different axes of the shaft system, realize automatic self-alignment, and avoid the shaft system from getting stuck; and after the self-alignment, the shaft system will be in light-load and stable operation, the friction force and friction resistance loss of the bearing will be reduced, and the noise will be effectively eliminated; and the elastic part has a dissipative effect on vibration, which can reduce the kinetic energy of the vibrating body, help to gradually weaken the vibration value, so that the vibration will not be amplified and transmitted back, so as to achieve the purpose of vibration reduction and noise reduction. The reduction of vibration is conducive to the stable operation of the shaft system and reduces the influence of the dynamic load of the bearing on the bearing life. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 is a cross-sectional view of the self-aligning bearing support of the present invention in use;

[0025] Figure 2 It is a cross-sectional view of the raised large-diameter section connecting ring body of the present invention;

[0026] Figure 3 yes Figure 2 Enlarged view of point A in the middle;

[0027] Figure 4 It is a cross-sectional view of the raised small diameter section connecting ring body of the present invention;

[0028] Figure 5 yes Figure 4 Enlarged view of point B in the middle;

[0029] Figure 6 is a cross-sectional view of a first form of the cutting groove in the present invention;

[0030] Figure 7 is a perspective view of a second form of the cutting groove in the present invention;

[0031] Figure 8 is a cross-sectional view of a second form of the cutting groove in the present invention;

[0032] Fig. 9 is a cross-sectional view of a third form of the cutting groove in the present invention;

[0033] Fig.10 is a cross-sectional view of a fourth form of the cutting groove in the present invention;

[0034] Fig.11 is a cross-sectional view of the convex ribs relative to each other in the present invention;

[0035] Fig.12 This is a cross-sectional view of the staggered arrangement of the convex ribs in the present invention.

[0036] Fig.13 is a cross-sectional view showing one set of rib groups in the present invention;

[0037] Fig.14 It is a simulated cross-sectional view of the self-aligning of the self-aligning bearing support in the present invention;

[0038] Fig.15 is a schematic diagram of a critical speed curve of a rotor system under different bearing stiffnesses in the prior art;

[0039] Fig.16 It is a schematic diagram of the unbalanced response value at the center position of the shaft system in the prior art;

[0040] Fig.17 It is a schematic diagram of the coaxiality dimensions of the shaft system in the prior art;

[0041] Fig.18 is a schematic diagram of stiffness coefficient and damping coefficient;.

[0042] In the figure:

[0043] 1. Bearing housing;

[0044] 2. Bearing bracket;

[0045] 3. Flexible support bracket; 31. Elastic member; 311. Protruding rib; 32. Damping member; 321. Ring body; 322. Protrusion; 323. Fixed body; 33. Gap; 34. Cutting groove;

[0046] 4. Bearings. DETAILED DESCRIPTION

[0047] The present invention will be further described in detail below in conjunction with the accompanying drawings and embodiments. It is to be understood that the specific embodiments described herein are only used to explain the present invention, rather than to limit the present invention. It should also be noted that, for ease of description, only parts related to the present invention, rather than all structures, are shown in the accompanying drawings.

[0048] In the description of the present invention, unless otherwise clearly specified and limited, the terms "connected", "connected", and "fixed" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0049] In the present invention, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may include that the first and second features are in direct contact, or may include that the first and second features are not in direct contact but are in contact through another feature between them. Moreover, a first feature being "above", "above" and "above" a second feature includes that the first feature is directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature. A first feature being "below", "below" and "below" a second feature includes that the first feature is directly below and obliquely below the second feature, or simply indicates that the first feature is lower in level than the second feature.

[0050] In the description of this embodiment, the terms "upper", "lower", "left", "right" and other directions or positional relationships are based on the directions or positional relationships shown in the drawings, and are only for the convenience of description and simplification of operation, rather than indicating or implying that the device or element referred to must have a specific direction, be constructed and operate in a specific direction, and therefore cannot be understood as limiting the present invention. In addition, the terms "first" and "second" are only used to distinguish in the description and have no special meaning.

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

[0052] The elastic member 31 is arranged around the bearing bracket 2, and the elastic member 31 can be squeezed for installation during installation, making the installation simpler; when there is misalignment (different axes) at both ends of the shaft system, the shaft system drives the bearing to squeeze the elastic member 31, so that the elastic member 31 produces radial deformation to eliminate the different axes of the shaft system, realize automatic self-alignment, and avoid the shaft system from getting stuck; and after the self-alignment, the shaft system is in a light-load and stable operation, the friction force and friction resistance loss of the bearing 4 are reduced, and the noise is effectively eliminated; and the elastic member 31 has a dissipative effect on vibration, which can reduce the kinetic energy of the vibrating body, help to gradually weaken the vibration value, so that the vibration will not be amplified and transmitted back, so as to achieve the purpose of vibration reduction and noise reduction. The reduction of vibration is conducive to the stable operation of the shaft system and reduces the influence of the dynamic load of the bearing on the life of the bearing 4.

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

[0054] It should be noted that the stiffness coefficient is the resistance to load deformation. The increment of liquid film force caused by unit displacement is calculated as follows:

[0055] Formula 1:

[0056] Formula 2:

[0057] Formula 3:

[0058] Formula 4:

[0059] The above formula 1 is that the component of the loading force in the X direction generates the displacement of the liquid film in the X direction; formula 2 is that the component of the loading force in the Y direction generates the displacement of the liquid film in the Y direction; formula 3 is that the component of the loading force in the X direction generates the displacement of the liquid film in the Y direction; formula 4 is that the component of the loading force in the Y direction generates the displacement of the liquid film in the X direction;

[0060] in,

[0061] F x_max and F x_min is the component of the applied force in the X direction, its maximum and minimum values;

[0062] F y_max and F y_min is the component of the loading force in the Y direction, its maximum and minimum values;

[0063] X max and X min The maximum and minimum values ​​of the displacement component in the X direction generated by the applied force.

[0064] Y max and Y min The maximum and minimum values ​​of the Y-direction displacement component generated by the applied force.

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

[0066]

[0067] The first formula above is that the component of the loading force in the X direction generates the velocity of the liquid film in the X direction; the second formula is that the component of the loading force in the Y direction generates the velocity of the liquid film in the Y direction; the third formula is that the component of the loading force in the X direction generates the velocity of the liquid film in the Y direction; the second formula is that the component of the loading force in the Y direction generates the velocity of the liquid film in the X direction

[0068] in,

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

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

[0071] The stiffness coefficient matrix is:

[0072]

[0073] The damping coefficient matrix is:

[0074]

[0075] In rotor dynamics analysis, the matrix of the four stiffness coefficients of the bearing support system (K xx , K yy , K xy , K yx ) and the matrix of four damping coefficients (C xx , C yy , C xy , C yx ). xy and yx are the cross stiffness coefficient and cross damping coefficient. Generally, no engineering analysis is done in rotor dynamics analysis, and only K is studied. xx , K yy Two stiffness coefficients and C xx , C yy Two damping coefficients. Fig.18 Schematic diagram of stiffness coefficient and damping coefficient shown;

[0076] Fig.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: displacement of the unbalanced response value at the shaft system node, m; Unbalance response value at the shafting node speed, m / s; Unbalanced response value at the axis node acceleration m 2 / s; [Q]: dynamic unbalanced force, N.

[0079] It should also be noted that the noise includes the noise generated by the friction process of the rolling elements of the bearing 4, including the noise of the air flow. The bearing load after the automatic self-aligning coaxiality is basically the weight of the shaft system. The radial load of the bearing 4 is reduced, and the axial force of the bearing 4 layout with a back-to-back structure is basically eliminated. Then the entire shaft system will be in a light-load and stable operation, and the friction force and friction resistance loss between the rolling elements and the raceway will be reduced, which will help to eliminate the mechanical friction noise. In addition, the lubricating oil at the bearing 4 can further reduce the friction resistance and wheel resistance loss, making the noise reduction more obvious. It should be noted here that the bearing housing 1 and the bearing bracket 2 are both prior art. It is only necessary to clarify that the bearing housing 1 has a first mounting hole for mounting the bearing bracket 2, and the bearing bracket 2 has a second mounting hole for inserting the bearing 4. The self-aligning bearing support in this application can be applied to ball bearings or sliding bearings.

[0080] like Figures 1 to 10 As shown, the damping member 32 is clamped between the elastic member 31 and the bearing bracket 2. Specifically, a plurality of embedded grooves are axially spaced apart on one side of the damping member 32 facing the bearing bracket 2, and a plurality of elastic members 31 are also provided. The plurality of elastic members 31 are embedded in the embedded grooves one by one, so that the elastic members 31 contact the bearing bracket 2.

[0081] Among them, the elastic member 31 is made of non-metallic polymer materials, such as nylon, PTFE, rubber and other soft non-metallic polymer materials; the damping member 32 is made of metal elastic materials, such as steel or steel alloy, etc. When the elastic member 31 is made of the above non-metallic polymer materials and is subjected to alternating stress (or vibration), it takes time for the movement of the chain macromolecules to overcome the friction resistance between the 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. After deformation, it means energy consumption, which just reduces the kinetic energy of the vibrating body and achieves the purpose of vibration reduction.

[0082] like Figure 2 and Figure 5As shown, in some embodiments, the damping member 32 includes a ring body 321 surrounding the bearing support 2, and the ring body 321 and the bearing housing 1 can be fixedly connected, including but not limited to welding, clamping or bolting. The inner ring surface of the ring body 321 is circumferentially spaced with a plurality of protrusions 322, and adjacent protrusions 322 form an embedded groove. The protrusion 322 includes an integrally formed large diameter section and a small diameter section, so that the protrusion 322 is T-shaped, that is, a limiting step is formed on the protrusion 322. In one embodiment, the large diameter section of the protrusion 322 is connected to the ring body 321, and the elastic member 31 is also T-shaped. During installation, the elastic member 31 is inserted into the embedded groove and overlapped at the limiting steps of two adjacent limiting protrusions 322. In the current structure, in order to ensure that the elastic member 31 has a larger elastic deformation space, there is a gap 33 between the elastic member 31 and the bottom of the embedded groove. The gap 33 can be but is not limited to 0.03mm-0.08mm. As Figure 4 As shown, in other alternative embodiments, the small diameter section of the protrusion 322 is connected to the ring body 321. In order to adapt to the above structure, the corresponding elastic member 31 is I-shaped, so that the protrusion 322 and the elastic member 31 are embedded in each other. In the current structure, in order to make the elasticity have a larger elastic deformation space, a gap 33 is provided between the side of the large diameter section of the protrusion 322 facing the bearing bracket 2 and the elastic member 31. The gap 33 can also be but not limited to 0.03mm-0.08mm; in addition, there can also be a certain spacing space for deformation between the small diameter section and the elastic member 31 and between two adjacent elastic members 31, without specific limitation.

[0083] like Figures 6 to 10 As shown, in some embodiments, the damping member 32 includes a plurality of fixed bodies 323 arranged at intervals along the circumference of the bearing support 2, and the fixed bodies 323 and the bearing housing 1 can be fixedly connected, including but not limited to welding, clamping or bolting. A groove is provided on the side of the fixed body 323 facing the bearing support 2, and the elastic member 31 is embedded in the groove; in order to ensure the stability of the embedding, the elastic member 31 is I-shaped, and the groove is also I-shaped; and a cutting groove 34 is provided on the fixed body 323, and its width direction is the same as the radial direction of the bearing support 2, so that when the elastic member 31 is squeezed by the bearing support 2, the pressure is transmitted to the fixed body 323, so that the fixed body 323 is deformed in the width direction of the cutting groove 34, so that the different axial degrees at both ends of the shaft system are offset by the common deformation of the elastic member 31 and the fixed body 323, and the centering is achieved. In the current embodiment, in order to facilitate the forming of the cutting groove 34, the cutting groove 34 is S-shaped or multi-segment discontinuous arc ( Figures 5 to 9Four different groove types are shown respectively, and the groove width of the cutting groove 34 can also be 0.03mm-0.08mm. The elastic effect of the damping member 32 is more helpful to gradually weaken the vibration value, so that the vibration will not be amplified and transmitted back. The reduction of the vibration value is conducive to the stable operation of the shaft system, thereby improving the life of the bearing 4.

[0084] like Figures 11 to 13 As shown, in some embodiments, the elastic member 31 is disposed between the bearing housing 1 and the bearing support 2, and the damping member 32 is disposed in the elastic member 31 to support the elastic member 31. Specifically, as Fig.10 and Fig.11 As shown, 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 with a plurality of ribs 311, the ribs 311 are located on the inner and outer sides of the damping member 32, and the protrusions 322 on the inner and outer annular surfaces can be arranged opposite to each other or staggered, without specific limitation. Fig.12 As shown, in other alternative embodiments, the elastic member 31 is annular and clamped between the bearing housing 1 and the bearing support 2. The inner ring surface of the elastic member 31 is provided with a plurality of rib groups, which are arranged at intervals along the inner ring surface of the elastic member 31, and each rib group is provided with a plurality of ribs 311, which are arranged at intervals along the axial direction of the elastic member 31, and the damping member 32 is located in the ribs 311 and protrudes into an arc toward one side of the bearing support 2, so that the damping member 32 of the above two settings is used to support the bearing support 2, so that the elastic member 31 adjusts the coaxiality of the shaft system when it is subjected to the force of the bearing support 2, and the damping member 32 inside the elastic member 31 realizes the support of the bearing support 2, and the damping member 32 can also realize elastic deformation, which helps to gradually weaken the vibration value. In addition, the size and number of the ribs 311 are not specifically limited, and can be customized according to different requirements such as the required compensation amount and critical speed.

[0085] For example, Fig.14 It is a simulation diagram of self-alignment. After the two self-aligning bearing brackets 2 are installed with bearings 4, they are defined as Z1 end and Z2 end respectively. The center lines of Z1 end and Z2 end are the positions of the axes. If Z2 end is eccentric, the axis system squeezes the damping member 32 at Z2 end. Assume that: if the groove width of the cutting groove 34 in the damping member 32 at Z1 end is 0.08mm, if the diameter eccentricity value of Z2 end is 0.05mm, the axis system squeezes the damping member 32 at Z2 end, and the top fixed body 323 in the damping member 32 produces a compression of 0.05mm, and the fixed bodies 323 on both sides produce a compression of 0.02mm, which compensates for the coaxiality and non-coaxiality problems of the axis system.

[0086] The present application also provides a centrifugal compressor, which includes a shaft system, a bearing 4 and two self-aligning bearing supports of any of the above forms. The bearing 4 is arranged in the second mounting hole of the bearing bracket 2, and the shaft system is installed on the bearing 4, so that it can automatically align, achieve vibration reduction and noise reduction, and improve service life.

[0087] Obviously, the above embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the embodiments of the present invention. For those skilled in the art, various obvious changes, readjustments and substitutions can be made without departing from the protection scope of the present invention. It is not necessary and impossible to list all the embodiments here. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention should be included in the protection scope of the claims of the present invention.

Claims

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

2. The self-aligning bearing support according to claim 1, characterized in that: The damping member (32) is clamped between the elastic member (31) and the bearing bracket (2).

3. The self-aligning bearing support according to claim 1, characterized in that: A plurality of embedding grooves are arranged at intervals in the circumferential direction on one side of the damping member (32) facing the bearing bracket (2), and a plurality of the elastic members (31) are embedded in the embedding grooves in a one-to-one correspondence.

4. The self-aligning bearing support according to claim 3, characterized in that: The damping member (32) comprises a ring body (321) surrounding the bearing support (2), the inner ring surface of the ring body (321) being provided with a plurality of protrusions (322) at intervals in the circumferential direction, and the embedding grooves are formed between adjacent protrusions (322).

5. The self-aligning bearing support according to claim 3, characterized in that: The damping member (32) comprises a plurality of fixed bodies (323) arranged at intervals along the circumference of the bearing support (2); the fixed body (323) is provided with the embedding groove on one side facing the bearing support (2); the elastic member (31) is embedded in the embedding groove; and the fixed body (323) is provided with a cutting groove (34) so ​​that the fixed body (323) can be deformed in the radial direction.

6. The self-aligning bearing support according to claim 1, characterized in that: The damping member (32) is arranged in the elastic member (31).

7. The self-aligning bearing support according to claim 6, characterized in that: The damping member (32) and the elastic member (31) are both annular; the inner annular surface and the outer annular surface of the elastic member (31) are both provided with a plurality of convex ribs (311) at circumferential intervals, and the convex ribs (311) are located on both inner and outer sides of the damping member (32).

8. The self-aligning bearing support according to claim 6, characterized in that: The elastic member (31) is annular, and the inner ring surface of the elastic member (31) is provided with a plurality of groups of convex rib groups, and the plurality of groups of convex rib groups are arranged at intervals along the circumferential direction of the inner ring surface of the elastic member (31), and each group of the convex rib groups contains a plurality of convex ribs (311), and the plurality of convex ribs (311) are arranged at intervals along the axial direction of the elastic member (31), and the damping member (32) is located in the convex ribs (311) and protrudes toward one side of the bearing bracket (2) in an arc shape.

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

10. A centrifugal compressor, characterized in that: The centrifugal compressor comprises a shaft system, a bearing (4) and two self-aligning bearing supports according to any one of claims 1 to 9, the bearing (4) is arranged in the second mounting hole, and the shaft system is mounted on the bearing (4).

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