CN208858777U - A kind of bearing damp device, transverse bearing, thrust bearing and rotor-support-foundation system - Google Patents
A kind of bearing damp device, transverse bearing, thrust bearing and rotor-support-foundation system Download PDFInfo
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- CN208858777U CN208858777U CN201821612816.XU CN201821612816U CN208858777U CN 208858777 U CN208858777 U CN 208858777U CN 201821612816 U CN201821612816 U CN 201821612816U CN 208858777 U CN208858777 U CN 208858777U
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Abstract
The utility model provides a kind of bearing damp device, transverse bearing, thrust bearing and rotor-support-foundation system, wherein, bearing damp device is for being installed in non-contact type bearing, the bearing damp device is made of shape-memory material, and the bearing damp device can adjust the gap between the non-contact type bearing and shaft by plastic deformation.In the utility model, by the way that bearing damp device is arranged in non-contact bearing, the bearing clearance between stationary parts and rotary part is adjusted and is corrected using the plastic deformation of bearing damp device itself to realize.In this way, so that the requirement of bearing machining precision and assembly precision reduces, and to keep more stable cooperation precision between the stationary parts of bearing and rotary part by being provided with above-mentioned bearing damp device within the bearing.
Description
Technical Field
The utility model relates to a bearing technical field especially relates to a bearing damper, journal bearing, thrust bearing and rotor system.
Background
Due to the characteristics of small friction coefficient and friction torque, high motion precision and the like, the non-contact bearing is more and more commonly used in some occasions with high rotating speed. But compared with a contact type mechanical bearing, the non-contact type mechanical bearing has small bearing clearance and higher processing difficulty.
For example, in the case of a non-contact radial bearing, a bearing gap between a bearing inner ring and a rotating shaft is narrow, which requires high machining precision and assembly precision of the rotating shaft and the bearing inner ring, otherwise, a shaft collision phenomenon is easily generated, and abrasion and damage are caused to the bearing. Also, in the case of a non-contact type thrust bearing, a bearing gap between the stator and the thrust disk is also narrow, and thus, high machining accuracy and high assembling accuracy are required for both the stator and the thrust disk to prevent collision and abrasion between the stator and the thrust disk.
SUMMERY OF THE UTILITY MODEL
The utility model provides a bearing damper, journal bearing, thrust bearing and rotor system to solve above-mentioned problem.
In a first aspect, the present invention provides a bearing damper for installation in a non-contact bearing, the bearing damper is made of a shape memory material, and the bearing damper can adjust a bearing gap between a stationary member and a rotating member through plastic deformation.
In a second aspect, the present invention provides a radial bearing for being installed in a rotating shaft, the radial bearing includes:
a bearing body;
the bearing inner ring is sleeved in the bearing body, and a bearing gap is formed between the bearing inner ring and a rotating shaft sleeved in the bearing inner ring;
and a bearing damper disposed between the bearing inner race and the bearing body, the bearing damper being the bearing damper described in the first aspect, the bearing damper being capable of undergoing plastic deformation under the action of the bearing inner race to adjust the bearing gap.
A third aspect of the present invention provides a thrust bearing for being installed in a rotating shaft, the thrust bearing comprising:
the thrust disc is connected to the rotating shaft;
the first stator and the second stator are arranged on the rotating shaft in a penetrating mode and are respectively arranged on two opposite sides of the thrust disc;
each of the first stator and the second stator comprises a stator body, a pressing plate and the bearing damper in the first aspect, the bearing damper is arranged between the stator body and the pressing plate, the pressing plate is arranged on one side of the stator body close to the thrust disc, and a bearing gap is formed between the pressing plate and the thrust disc;
wherein the bearing damper is capable of undergoing plastic deformation under the action of the pressure plate to adjust the bearing clearance.
In a fourth aspect, the present invention provides a rotor system, including a rotating shaft, a thrust bearing and at least two radial bearings, wherein the thrust bearing and the at least two radial bearings are both mounted on the rotating shaft, and the thrust bearing and the at least two radial bearings are both non-contact bearings;
wherein at least one of the at least two radial bearings is the radial bearing of the second aspect; and/or the thrust bearing is the thrust bearing of the third aspect.
The utility model discloses in, through set up the bearing attenuator in non-contact bearing to the realization utilizes the plastic deformation of bearing attenuator self to adjust and correct the bearing clearance between static part and the rotary part. In this way, by providing the bearing damper in the bearing, the requirements for the machining accuracy and the assembling accuracy of the bearing are reduced, and the stable matching accuracy between the stationary member and the rotating member of the bearing is maintained.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required to be used in the description of the embodiments of the present invention will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without inventive labor.
FIG. 1 is one of the schematic structural views of a bearing damper;
FIG. 2 is a second schematic view of a bearing damper;
FIG. 3 is a schematic view of a radial bearing;
FIG. 4 is a cross-sectional view taken along line A-A of FIG. 3;
FIG. 5 is a schematic view showing a dynamic pressure generating groove of the radial bearing;
fig. 6 is a schematic structural view of another dynamic pressure generating groove of the radial bearing;
FIG. 7 is a schematic view of a thrust bearing;
FIG. 8 is a schematic view showing a dynamic pressure generating groove of the thrust bearing;
FIG. 9 is a schematic view showing another dynamic pressure generating groove structure of the thrust bearing;
fig. 10 to 27 are schematic structural views of various horizontal rotor systems provided in embodiments of the present invention;
fig. 28 to 45 are schematic structural diagrams of various vertical rotor systems provided in embodiments of the present invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, not all, of the embodiments of the present invention. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.
In a first aspect, embodiments of the present invention provide a bearing damper, as shown in fig. 1 to 2, for being installed in a non-contact bearing, such as a non-contact radial bearing, a non-contact thrust bearing, and the like. The bearing damper is made of a shape memory material, and is capable of adjusting a bearing clearance between a stationary member and a rotating member by plastic deformation.
The embodiment of the utility model provides an in, realize adjusting and correcting the bearing clearance between static part and the rotary part through the plastic deformation of bearing attenuator self to make the requirement of bearing machining precision and assembly precision reduce. Because the bearing damper is made of the shape memory material, the shape of the bearing damper is kept unchanged after the bearing damper is subjected to plastic deformation, so that the stable matching precision between the static part and the rotating part of the bearing is kept.
The utility model discloses bearing damper can be used for journal bearing, also can be used to thrust bearing.
When the bearing damper is used for the radial bearing, the bearing damper can adjust the bearing clearance between the radial bearing and the rotating shaft through plastic deformation, at the moment, the static part is the radial bearing, and the rotating part is the rotating shaft sleeved in the radial bearing. When the bearing damper is used for the radial bearing, the coaxiality between the radial bearing and the rotating shaft can be corrected, the processing precision and the assembling precision of the radial bearing and the rotating shaft are reduced, and the shaft collision phenomenon is reduced.
When the bearing damper is used for a thrust bearing, the bearing damper can adjust a bearing gap between a stator and a thrust disc of the thrust bearing through plastic deformation, and at this time, the stationary part is the stator of the thrust bearing, and the rotating part is the thrust disc of the thrust bearing. When the bearing damper is used for the thrust bearing, the parallelism between the thrust disc of the thrust bearing and the stator can be corrected, so that the processing precision and the assembly precision of the thrust disc of the thrust bearing and the stator on the flatness can be reduced.
With respect to the specific embodiments of the bearing damper for use in the radial bearing and the thrust bearing, detailed description will be given later.
The bearing damper can be made of shape memory metal or shape memory polymer, wherein the shape memory metal can be any one of titanium-nickel alloy, copper-zinc alloy, copper-aluminum-nickel alloy, copper-molybdenum-nickel alloy and copper-gold-zinc alloy. If the working environment of the bearing is a high temperature environment, the bearing damper 530 may be made of a shape memory metal that is resistant to high temperatures (e.g., above 300 ℃).
The dynamic force for generating plastic deformation of the bearing damper is derived from the air film pressure between the non-contact bearing and the rotating shaft, the gravity of the rotating shaft and the common acting force of the load of the rotating shaft on the bearing inner parts. Hereinafter, the description will be specifically made in conjunction with the respective bearings.
The embodiment of the present invention provides an embodiment, the bearing damper can include at least two adjusting units 531, the bearing damper can be a whole device formed by continuously setting at least two adjusting units, and also can include at least two independently set adjusting members, the adjusting member can include at least one adjusting unit 531, for example, one adjusting unit 531 is an adjusting member, two adjusting units 531 form an adjusting member, three adjusting units 531 form an adjusting member, and so on. It is understood that when one adjusting unit 531 forms one adjusting member, the adjusting unit 531 is equivalent to the adjusting member. When the bearing damper is an integral device formed by continuously arranging at least two adjusting units, on one hand, the installation can be faster; on the other hand, bearings of different sizes or types may need to be provided with different types of bearing dampers, and the application range is limited. When the bearing damper includes at least two independently provided adjusting members, the independently provided adjusting members may be applied to any bearing as long as an appropriate number of adjusting members are configured according to the size or kind of the bearing, or a plurality of adjusting members are arranged in a shape suitable for the bearing.
In the embodiment of the present invention, the adjusting unit 531 may be a half-shell structure, including the protruding portion 532 and the supporting portion 533, the protruding portion 532 and the supporting portion 533 are integrally formed. The outer surface of the protruding portion 532 is a smooth arc-shaped curved surface, and the supporting portion 533 extends smoothly from the protruding portion 532 to the periphery. The entire adjustment unit 531 may have the boss 532 as a portion where the adjustment unit 531 is plastically deformed, and the support portion 533 as a portion where the entire adjustment unit 531 is supported. The adjustment unit 531 is provided as the half-shell structure, so that the adjustment unit 531 is in a stable state before and after being stressed.
In addition to the half shell structure described above, the adjustment unit 531 may also have a wave structure, a zigzag structure, a spherical shell structure, a hemispherical shell structure, or the like.
In the embodiment of the present invention, in order to make the adjusting unit 531 have better plastic deformation performance, the thickness of the adjusting unit 531 should not be too large; in order to make the adjusting unit 531 have stable mechanical properties, the height of the adjusting unit 531 should not be too large. The height H of the adjustment unit 531 may be between 1mm and 3mm, and the thickness L of the adjustment unit 531 may be between 0.1mm and 0.3 mm.
The embodiment of the utility model provides an in, through set up the bearing attenuator in non-contact bearing to the realization utilizes the plastic deformation of bearing attenuator self to adjust and correct the bearing clearance between static part and the rotary part. In this way, by providing the bearing damper in the bearing, the requirement for the machining accuracy of the bearing is reduced, and the stable fitting accuracy between the stationary member and the rotating member of the bearing is maintained. Moreover, the bearing damper is simple in structure, convenient to produce and process, free of changing the structure of the original bearing and suitable for large-scale application.
In a second aspect, an embodiment of the present invention provides a radial bearing, as shown in fig. 3 to 6, a radial bearing 500 for being installed on a rotating shaft 100, the radial bearing 500 including:
a bearing body 520;
a bearing inner ring 540 sleeved on the rotating shaft 100, a bearing gap is formed between the bearing inner ring 540 and the rotating shaft 100, and the bearing inner ring 540 is sleeved in the bearing body 520 and can move in the bearing body 520;
and a bearing damper 530 disposed between the bearing inner race 540 and the bearing body 520, wherein the bearing damper 530 may be disposed to be adjacent to an inner diameter surface of the bearing body 520, the bearing damper 530 is made of a shape memory material, and the bearing damper 530 may be plastically deformed by the bearing inner race 540 to adjust a bearing gap.
The embodiment of the utility model provides an in, journal bearing 500 installs in pivot 100, after pivot 100 starts, journal bearing 500's bearing inner circle 540 adjusts the position of self under the combined action of air film pressure, pivot gravity and pivot load to make the bearing clearance between pivot 100 and the bearing inner circle 540 satisfy the steady moving demand of bearing. In this way, the fitting accuracy, i.e., the coaxiality, between the radial bearing 500 and the rotating shaft 100 is adjusted or corrected.
In the above process, the bearing damper 530 is subjected to corresponding plastic deformation under the pressing action of the bearing inner ring 540, so that the bearing inner ring 540 is supported at a new balance position, and the adjustment or correction of the coaxiality between the rotating shaft 100 and the bearing inner ring 540 is completed, so as to avoid the abrasion and damage of the rotating shaft 100 to the bearing inner ring 540.
As mentioned above, the bearing damper 530 may include at least two adjusting units 531, and the bearing damper may be an integral device formed by continuously arranging the at least two adjusting units, or may include at least two independently arranged adjusting members, and the adjusting members may include at least one adjusting unit 531.
As described above, the adjustment unit 531 has a half-shell structure, and includes the protrusion 532 and the support 533, and the protrusion 532 and the support 533 are integrally formed; the convex portion 532 faces the bearing inner race 540, and the support portion 533 is attached to the inner diameter surface of the bearing body 520; the protruding portion 532 can be plastically deformed by the bearing inner race 540 to adjust a bearing gap, i.e., a gap between the bearing inner race 540 and the rotating shaft 100.
At the initial operation stage of the bearing after the rotation shaft 100 is started, the bearing inner ring 540 moves in the radial direction or swings around the axis at a certain angle in the axial direction to adjust the coaxiality of the rotation shaft 100 and the bearing inner ring 540 until the bearing stable operation state is reached. In the above adjustment process, since the adjustment unit 531 is made of the memory metal, the convex portion 532 of the adjustment unit 531 on the pressed side is pressed to be plastically deformed, and is held in the deformed state. The coaxiality between the radial bearing and the rotating shaft can be corrected through the deformation of the adjusting unit 531, so that the processing precision and the assembling precision of the bearing inner ring 540 and the rotating shaft 100 can be reduced, and the occurrence of the shaft collision phenomenon is reduced.
As described above, the height H of the adjustment unit 531 may be between 1mm and 3mm, and the thickness L of the adjustment unit 531 may be between 0.1mm and 0.3 mm.
In the embodiment of the present invention, the adjusting members may be circumferentially and uniformly distributed along the inner diameter surface of the bearing body 520 to form the ring-shaped bearing dampers 530; the adjusting members may also be axially and uniformly distributed along the inner diameter surface of the bearing body 520 to form the linear arrangement of the bearing dampers 530; the adjustment members may also be circumferentially and evenly distributed along the inner diameter surface of the bearing body 520, and axially and evenly distributed along the inner diameter surface of the bearing body 520 to form a multi-ring bearing damper 530. The setting mode of the adjusting component can enable the adjusting process of the bearing clearance to be more stable, and the bearing clearance is more uniform.
In the embodiment of the present invention, before the radial bearing 500 operates for the first time, a protective layer may be disposed at the position of the rotating shaft 100 corresponding to the radial bearing 500, so as to protect the mating surfaces of the rotating shaft 100 and the radial bearing 500. Specifically, protective layers may be provided at both ends of the rotating shaft 100 corresponding to the position where the radial bearing 500 is installed. Thus, during the starting or calibration phase of the rotating shaft 100, the protective layer first rubs against the inner bearing ring 540, thereby protecting the mating surface of the rotating shaft 100 and the inner bearing ring 540. The protective layer may be made of teflon, graphite, babbitt metal, etc., and may be disposed on the rotating shaft 100 in a coating manner.
The embodiment of the present invention provides a radial bearing 500 which can be any one of gas bearings such as dynamic pressure gas bearing, static pressure gas bearing, hybrid dynamic and static pressure gas bearing.
When the radial bearing 500 is a dynamic pressure gas bearing, a dynamic pressure generating groove 541 is provided on an inner diameter surface of the bearing inner race 540 or a circumferential surface of the rotating shaft 100 facing the bearing inner race 540.
The dynamic pressure generating grooves 541 may be formed by forging, rolling, etching, or punching. To facilitate the machining of the dynamic pressure generating grooves 541, the bearing inner race 540 may be made of a stainless steel material. When the rotating shaft 100 rotates at a high speed with respect to the bearing inner race 540, an aerodynamic pressure is generated in the dynamic pressure generating groove 541, and the rotating shaft 100 floats. The amount of floating varies depending on the angle, groove width, number of grooves, length, depth, and flatness of the dynamic pressure generating grooves 541. The magnitude of the aerodynamic pressure generated in the dynamic pressure generating groove 541 depends on the rotation speed of the rotating shaft 100 and the bearing gap. The parameters of the dynamic pressure generating groove 541 may be designed according to actual conditions.
The dynamic pressure generating grooves 541 may be disposed at a middle portion of the rotating shaft 100 corresponding to the circumferential surface of the bearing inner race 540, or may be disposed as two independent dynamic pressure generating grooves 541 symmetrically disposed at both sides of the middle portion; the dynamic pressure generating grooves 541 may be provided in the middle of the inner diameter surface of the bearing inner race 540, or may be provided as two independent dynamic pressure generating grooves 541 symmetrically distributed at both ends of the inner diameter surface of the bearing inner race 540.
In the embodiment of the present invention, the dynamic pressure generating grooves 541 may be arranged in a matrix. Thus, the air film is favorably distributed in the bearing gap more uniformly.
In the embodiment of the present invention, the dynamic pressure generating groove 541 may be a V-shaped groove disposed continuously or at intervals. Thus, the rotating shaft 100 can be contactlessly held in a desired manner in the case where the rotating shaft 100 is rotated in the forward direction or in the reverse direction, so that the rotating shaft 100 has advantages of high load capacity and good stability. The dynamic pressure generating grooves 541 may be provided as chevron-shaped grooves or grooves of other shapes, in addition to the V-shaped grooves.
When the radial bearing 500 is a static pressure gas bearing, the radial bearing is further provided with a static pressure air inlet orifice 521 for communicating the bearing gap with an external air source, and the static pressure air inlet orifice 521 is used for conveying the external air source into the bearing gap. The flow diameter of the static pressure intake orifice 521 can be adjusted according to actual working conditions such as air quantity requirements.
The embodiment of the utility model provides an in, static pressure air inlet throttle 521 can pass bearing body 520, bearing attenuator 530 and bearing inner race 540 in proper order, with bearing clearance and external air supply intercommunication.
In the embodiment of the present invention, the static pressure intake orifice 521 is divided into at least two branches in the radial bearing 500 to communicate with the bearing gap. In this way, the gas film pressure in the bearing gap of the radial bearing 500 can be made more uniform. The static pressure intake orifice 521 and the circulation diameter of each branch can be adjusted according to actual working conditions such as air quantity requirements.
When the radial bearing 500 is a hybrid gas bearing, the radial bearing 500 is provided with both the dynamic pressure generating grooves 541 and the static pressure intake orifices 521. Since the dynamic pressure generating groove 541 and the static pressure intake orifice 521 have been described separately, they will not be described in detail here to avoid redundancy.
The embodiment of the present invention provides a radial bearing 500 can also be a gas-magnetic hybrid bearing, i.e. on the basis of any one of the above-mentioned gas bearings, a plurality of magnetic members are provided on the bearing body 520, and the magnetic members can be correspondingly provided on the rotating shaft 100, so that the rotating shaft 100 can move in the radial direction of the rotating shaft 100 under the magnetic force action of the plurality of magnetic members.
In a third aspect, an embodiment of the present invention provides a thrust bearing, as shown in fig. 7 to 9, a thrust bearing 700 for being installed on a rotating shaft 100, the thrust bearing 700 including:
a thrust disc 710, the thrust disc 710 being connected to the rotating shaft 100;
the first stator 720 and the second stator 730 are arranged on the rotating shaft 100 in a penetrating manner, and the first stator 720 and the second stator 730 are respectively arranged on two opposite sides of the thrust disc 710;
each of the first stator 720 and the second stator 730 comprises a stator body, a pressure plate and a bearing damper 530, wherein the bearing damper 530 is arranged between the stator body and the pressure plate, the pressure plate is arranged on one side of the stator body close to the thrust disc, and a bearing gap is formed between the pressure plate and the thrust disc 710;
wherein the bearing damper 530 is made of a shape memory material, and the bearing damper 530 can be plastically deformed by the pressing plate to adjust the bearing gap.
Specifically, the first stator 720 includes a first stator body 722, a bearing damper 530, and a first pressure plate 723, the bearing damper 530 is mounted on an end surface of the first stator body 722 facing the thrust plate 710, and the first pressure plate 723 is mounted in close contact with the bearing damper 530; the second stator 730 includes a second stator body 732, a bearing damper 530, and a second presser plate 733, the bearing damper 530 is attached to an end surface of the second stator body 732 facing the thrust plate 710, and the second presser plate 733 is attached in close contact with the bearing damper 530.
In the initial operation stage of the bearing after the rotating shaft 100 is started, the first pressing plate 723 and the second pressing plate 733 adjust their positions under the combined action of the air film pressure and the axial load of the rotating shaft 100, so that the clearances among the first stator 720, the second stator 730 and the thrust disc 710 meet the requirement of smooth operation of the bearing. In the process, the bearing damper 530 is correspondingly plastically deformed under the pressing action of the first pressing plate 723 or the second pressing plate 733, so that the first pressing plate 723 and the second pressing plate 733 are supported at new balance positions, and the correction of the parallelism between the thrust disc 710 and the first stator 720 and the second stator 730 is completed, so that the abrasion and collision between the thrust disc 710 and the first stator 720 and the second stator 730 are avoided. This completes the correction of the fitting accuracy, i.e., parallelism, between the thrust disk 710 of the thrust bearing 700 and the first stator 720 and the second stator 730.
As mentioned above, the bearing damper 530 may include at least two adjusting units 531, and the bearing damper may be an integral device formed by continuously arranging the at least two adjusting units, or may include at least two independently arranged adjusting members, and the adjusting members may include at least one adjusting unit 531.
As described above, the adjustment unit 531 has a half-shell structure, and includes the boss 532 and the support portion 533, and the boss 532 and the support portion 533 are integrally formed. For the first stator 720, the protruding portion 532 faces the first pressing plate 723, and the supporting portion 533 is attached to the first stator body 722; the second stator 730 has the projection 532 facing the second presser plate 733, and the support portion 533 is attached to the second stator body 732. The convex portion 532 can be plastically deformed by the first presser plate 723 or the second presser plate 733 to adjust the bearing gap.
In the initial operation stage of the bearing after the rotating shaft 100 is started, the first pressing plate 723 or the second pressing plate 733 moves in the axial direction or swings around the axis by a certain angle to adjust the parallelism between the thrust disc 710 and the first stator 720 and the second stator 730 until a bearing smooth operation state is reached. In the above adjustment process, since the adjustment unit 531 is made of the memory metal, the convex portion 532 of the adjustment unit 531 on the pressed side is pressed to be plastically deformed, and is held in the deformed state. The parallelism between the thrust disc 710 and the first and second stators 720 and 730 can be corrected by the deformation of the adjustment unit 531, so that the machining accuracy and the assembling accuracy of the thrust disc 710, the first and second stators 720 and 730 in the flatness can be reduced.
As described above, the height H of the adjustment unit 531 may be between 1mm and 3mm, and the thickness L of the adjustment unit 531 may be between 0.1mm and 0.3 mm.
In the embodiment of the present invention, the adjusting members may be respectively and uniformly distributed along the circumferential direction of the end surfaces of the first stator body 722 and the second stator body 732 to form the ring-shaped bearing dampers 530; the adjusting components can also be uniformly distributed along the end surfaces of the first stator body 722 and the second stator body 732 in the radial direction to form the bearing dampers 530 which are arranged in a linear shape; the adjusting members may also be uniformly distributed along the circumferential direction of the end surfaces of the first stator body 722 and the second stator body 732, and radially distributed along the end surfaces of the first stator body 722 and the second stator body 732, so that the adjusting members are distributed with multiple rings along the end surfaces of the first stator body 722 and the second stator body 732, respectively, to form the multi-ring bearing damper 530. The setting mode of the adjusting component can enable the adjusting process of the bearing clearance to be more stable, and the bearing clearance is more uniform.
The embodiment of the utility model provides an in thrust bearing 700 can be any kind among the gas bearings such as dynamic pressure gas bearing, static pressure gas bearing, hybrid gas bearing.
When the thrust bearing 700 is a dynamic pressure gas bearing, a dynamic pressure generating groove 741 is provided on an end surface of the pressure plate facing the thrust disk 710 or an end surface of the thrust disk 710 facing the pressure plate. For the first stator 720, a dynamic pressure generating groove 741 is provided on an end surface of the first presser plate 723 facing the thrust disk 710 or an end surface of the thrust disk 710 facing the first presser plate 723; in the second stator 730, a dynamic pressure generating groove 741 is provided in an end surface of the second presser plate 733 facing the thrust disk 710 or an end surface of the thrust disk 710 facing the second presser plate 733.
The dynamic pressure generating groove 741 may be formed by forging, rolling, etching, or punching. To facilitate the machining of the dynamic pressure generating grooves 741, the first pressure plate 723 and the second pressure plate 733 may be made of a stainless steel material. When the thrust disk 710 rotates at a high speed, the flowing gas existing in the bearing gap is pressed into the dynamic pressure generating groove 741, thereby generating pressure to achieve non-contact holding of the thrust disk 710 in the axial direction. The magnitude of the pressure generated by the dynamic pressure generating grooves 741 varies depending on the angle, width, number, length, depth, and flatness of the dynamic pressure generating grooves 741. The magnitude of the aerodynamic pressure generated in the dynamic pressure generating groove 741 is also related to the rotational speed of the thrust disk 710 and the bearing gap. The parameters of the dynamic pressure generating groove 741 may be designed according to actual conditions.
In the embodiment of the present invention, the dynamic pressure generating grooves 741 may be arranged in a radial or concentric manner. Thus, the air film is favorably distributed in the bearing gap more uniformly.
In the embodiment of the present invention, the dynamic pressure generating groove 741 may include a first spiral groove 7411 and a second spiral groove 7412, the first spiral groove 7411 surrounds the second spiral groove 7412, the spiral directions of the first spiral groove 7411 and the second spiral groove 7412 are opposite, and one end of the first spiral groove 7411 close to the second spiral groove 7412 is connected or disconnected with one end of the second spiral groove 7412 close to the first spiral groove 7411.
Wherein, the distance from the end of the first spiral groove 7411 close to the second spiral groove 7412 to the axial center of the rotating shaft 100 is equal to the distance from the end of the first spiral groove 7411 close to the second spiral groove 7412 to the outer peripheral edges of the first pressing plate 723 and the second pressing plate 733 or the thrust disc 710. Alternatively, the distance from the end of the second spiral groove 7412 close to the first spiral groove 7411 to the axial center of the rotary shaft 100 is equal to the distance from the end of the second spiral groove 7412 close to the first spiral groove 7411 to the outer peripheral edges of the first presser plate 723 and the second presser plate 733 or the thrust disc 710.
In the embodiment of the present invention, by adopting the above-mentioned setting mode of the dynamic pressure generating groove 741, the thrust disk 710 can be maintained in a desired manner in a non-contact manner under the condition of the forward rotation or the reverse rotation of the rotating shaft 100, so that the rotating shaft 100 has the advantages of high load capacity and good stability.
When the thrust bearing 700 is a static pressure gas bearing, the first stator 720 is further provided with a first static pressure intake orifice 721 for communicating the bearing gap with an external air source, and the second stator 730 is further provided with a second static pressure intake orifice 731 for communicating the bearing gap with the external air source. The first static pressure intake orifice 721 and the second static pressure intake orifice 731 are used to feed the external air supply into the bearing gap, respectively. The flow diameters of the first static pressure intake orifice 721 and the second static pressure intake orifice 731 may be adjusted according to actual conditions such as air quantity demand.
In the embodiment of the present invention, the first static pressure intake orifice 721 may sequentially pass through the first stator body 722, the bearing damper 530 and the first pressing plate 723 to communicate the bearing gap with the external air source; the second static pressure intake orifice 731 may pass through the second stator body 732, the bearing damper 530, and the second pressure plate 733 in sequence, communicating the bearing gap with an external air supply.
When the thrust bearing 700 is a hybrid gas bearing, the thrust bearing 700 is provided with both the dynamic pressure generating groove 741 and the first and second static pressure intake orifices 721 and 731. Since the dynamic pressure generating groove 741, the first static pressure intake orifice 721, and the second static pressure intake orifice 731 have been described separately, detailed descriptions thereof will be omitted to avoid redundancy.
The thrust bearing 700 of the embodiment of the present invention can also be a gas-magnetic hybrid bearing, that is, on the basis of any one of the above-mentioned gas bearings, a first magnetic member is provided on the thrust disk 710, a plurality of second magnetic members are further provided in the first stator body 722 and the second stator body 732, and the thrust disk 710 can move in the axial direction of the rotating shaft 100 under the action of the magnetic force between the first magnetic member and the plurality of second magnetic members.
In a fourth aspect, embodiments of the present invention provide a rotor system using the radial bearing in the second aspect or the thrust bearing in the third aspect, where the rotor system may be a horizontal rotor system or a vertical rotor system.
In an embodiment of the present invention, a rotor system includes a rotating shaft and at least two radial bearings, the at least two radial bearings are sleeved on the rotating shaft, and the at least two radial bearings are non-contact bearings;
wherein at least one of the at least two radial bearings is any one of the radial bearings provided in the second aspect.
Optionally, the shaft body of the rotating shaft is of an integrated structure, and the rotating shaft is horizontally arranged or vertically arranged;
the rotating shaft is sequentially provided with a motor, a gas compressor and a turbine;
the rotating shaft is also provided with a thrust bearing, and the thrust bearing is a non-contact bearing;
the thrust bearing is arranged at a preset position on one side of the turbine close to the compressor, and the preset position is a position which can enable the gravity center of the rotor system to be located between two radial bearings which are farthest away from each other in the at least two radial bearings.
Further, the thrust bearing in the rotor system may be any one of the thrust bearings provided in the third aspect.
In an embodiment of the present invention, a rotor system includes a rotating shaft and any one of thrust bearings provided by the third aspect, and the thrust bearing is installed on the rotating shaft.
Optionally, the shaft body of the rotating shaft is of an integrated structure, and the rotating shaft is horizontally arranged or vertically arranged;
the rotating shaft is sequentially provided with a motor, a gas compressor and a turbine;
the rotating shaft is also provided with at least two radial bearings which are non-contact bearings;
the thrust bearing is arranged at a preset position on one side of the turbine close to the compressor, and the preset position is a position which can enable the gravity center of the rotor system to be located between two radial bearings which are farthest away from each other in the at least two radial bearings.
Further, the radial bearing in the rotor system may be any one of the radial bearings provided in the second aspect.
Various embodiments of a horizontal rotor system are provided below.
As shown in fig. 10, a horizontal rotor system comprises a rotating shaft 100, a turbine 200, a compressor 300, a motor 400, a first radial bearing 500, a second radial bearing 600 and a thrust bearing 700, wherein the rotating shaft 100 passes through the first radial bearing 500, the thrust bearing 700, the motor 400, the compressor 300, the second radial bearing 600 and the turbine 200 which are arranged in sequence, the rotating shaft 100 rotates in the first radial bearing 500, a stator of the thrust bearing 700, a stator of the motor 400 and the second radial bearing 600, the rotating shaft 100 is fixedly connected with a thrust disc of the thrust bearing 700 and a turbine of the turbine 200 and a compression wheel of the compressor 300, the mass and/or axial position of the thrust bearing 700 are adjusted according to the weight of the whole horizontal rotor system (including the motor 400), so that the gravity center of the whole rotor system is located between the first radial bearing 500 and the second radial bearing 600, preferably on the compressor 300.
As shown in fig. 11, when the turbine weight of the turbine is too large and the thrust bearing 700 is disposed between the first radial bearing 500 and the motor 400, and the center of gravity of the entire horizontal rotor system still cannot fall between the two farthest radial bearings, the horizontal rotor system of embodiment 2 is adopted, which is different from the horizontal rotor system of embodiment 1 only in that the thrust bearing 700 is further moved forward and located at the front end of the first radial bearing 500 (where the direction from the motor to the turbine is from front to back).
The horizontal rotor system shown in fig. 10 to 11 is suitable for heavy turbine wheels, such as those made of metal.
For a lightweight turbine, such as a turbine made of ceramic material, ceramic fiber composite material, etc., when the diameter of the thrust disk of the thrust bearing 700 is small and does not block the inlet of the gas turbine, a horizontal rotor system as shown in fig. 12 is used, which is different from the horizontal rotor system shown in fig. 10 only in that the position of the thrust bearing 700 is moved backward so as to be located between the motor 400 and the compressor 300, and the diameter of the thrust disk of the thrust bearing 700 is small and does not block the inlet of the gas turbine.
In order to improve the stability of the entire horizontal rotor system, an improvement is made on the horizontal rotor system shown in fig. 10 to 12. For the horizontal rotor system shown in fig. 10 and 11, a third radial bearing 800 is added between the motor 400 and the compressor 300, and for the horizontal rotor system shown in fig. 12, a third radial bearing 800 is provided between the thrust bearing 700 and the compressor 300 or between the motor 400 and the thrust bearing 700, see in particular fig. 13 to 16.
When the weight of the motor is too heavy and cannot pass through the forward thrust bearing, so that the gravity center of the whole rotor system is located between the 2 farthest radial bearings, the coupling is cancelled on the horizontal rotor system with the original cantilever type structure, the radial bearings are arranged at the two ends of the whole rotor system, the whole rotor system is in a spindle shape, so that the structure of the whole rotor system is stable, the instability during high-speed rotation is avoided, and the requirement of the current gas turbine on high rotation speed is met.
As shown in fig. 17, a horizontal rotor system includes a rotating shaft 100, a turbine 200, a compressor 300, a motor 400, a first radial bearing 500, a second radial bearing 600, a thrust bearing 700, and a fourth radial bearing 801, wherein the rotating shaft 100 passes through the first radial bearing 500, the motor 400, the compressor 300, the thrust bearing 700, the second radial bearing 600, the turbine 200, and the fourth radial bearing 801 which are arranged in sequence, the rotating shaft 100 rotates in the first radial bearing 500, the stator of the motor 400, the stator of the thrust bearing 700, the second radial bearing 600, and the fourth radial bearing 801, and the rotating shaft 100 is fixedly connected with a thrust disc of the thrust bearing 700, and a turbine of the turbine 200 and a compression wheel of the compressor 300.
To improve the stability of the entire horizontal rotor system, an improvement is made on the horizontal rotor system shown in fig. 17, and a third radial bearing 800 is added between the motor 400 and the compressor 300, see fig. 18 in particular.
Preferably, the first radial bearing 500, the second radial bearing 600, the third radial bearing 800 and the fourth radial bearing 801 are all non-contact radial bearings.
Preferably, the second radial bearing 600 and the fourth radial bearing 801 are hybrid dynamic and static radial bearings combining a hydrostatic gas radial bearing and a hydrodynamic gas radial bearing.
Preferably, the first radial bearing 500 and the third radial bearing 800 are air-magnetic hybrid radial bearings.
Preferably, the motor 400 is a fluid dynamic bearing motor, and a dynamic pressure generating groove is formed in a portion of the rotating shaft 100 corresponding to the motor 400.
Preferably, the end face of the turbine 200 adjacent to the second radial bearing 600 is provided with a thermally insulating material, such as aerogel.
Preferably, the compressor 300 is a centrifugal compressor.
Preferably, the turbine is a centrifugal turbine.
Preferably, on the basis that the second radial bearing 600 is a hybrid dynamic-static radial bearing combining a hydrostatic gas radial bearing and a hydrodynamic gas radial bearing, a magnetic element is added to form a hybrid gas-magnetic radial bearing, which has a structure substantially the same as that of the first radial bearing 500 and the third radial bearing 800 when they are hybrid gas-magnetic bearings, except that no magnetic element is disposed at a position of the second radial bearing 600 close to the turbine 200, because the magnetic element does not resist high temperature, and structural diagrams of a horizontal rotor system in which the second radial bearing 600 is configured as a hybrid gas-magnetic radial bearing are shown in fig. 19 to 27, respectively, corresponding to fig. 10 to 18.
Various embodiments of a vertical rotor system are provided below.
As shown in fig. 28, a vertical rotor system comprises a rotating shaft 100, a turbine 200, a compressor 300, a motor 400, a first radial bearing 500, a second radial bearing 600 and a thrust bearing 700, wherein the rotating shaft 100 passes through the first radial bearing 500, the thrust bearing 700, the motor 400, the compressor 300, the second radial bearing 600 and the turbine 200 which are arranged in sequence, the rotating shaft 100 rotates in the first radial bearing 500, a stator of the thrust bearing 700, a stator of the motor 400 and the second radial bearing 600, the rotating shaft 100 is fixedly connected with a thrust disc of the thrust bearing 700 and a turbine of the turbine 200 and a compression wheel of the compressor 300, the mass and/or axial position of the thrust bearing 700 are adjusted according to the weight of the whole vertical rotor system (including the motor 400), so that the gravity center of the whole rotor system is located between the first radial bearing 500 and the second radial bearing 600, preferably on the compressor 300.
As shown in fig. 29, it differs from the vertical rotor system shown in fig. 28 only in that the thrust bearing 700 is moved forward, at the front end of the first radial bearing 500 (where the direction of the motor to the turbine is from front to back).
When the diameter of the thrust disk of the thrust bearing 700 is small and does not block the inlet of the gas turbine, the vertical rotor system as shown in fig. 30 is adopted, which is different from the vertical rotor system as shown in fig. 28 only in that the position of the thrust bearing 700 is moved backward so as to be located between the motor 400 and the compressor 300, and the diameter of the thrust disk of the thrust bearing 700 is small and does not block the inlet of the gas turbine.
In order to improve the stability of the whole vertical rotor system, an improvement is made on the vertical rotor system shown in fig. 28 to 30. For the vertical rotor system shown in fig. 28 and 29, a third radial bearing 800 is added between the motor 400 and the compressor 300; for the vertical rotor system shown in fig. 30, a third radial bearing 800 is provided between the thrust bearing 700 and the compressor 300 or between the motor 400 and the thrust bearing 700, see in particular fig. 31 to 34.
Under a special working condition, the thrust bearing cannot be moved forward, and then the radial bearings are arranged at the two ends of the whole rotor system, so that the whole rotor system is in a spindle shape, and the structure of the whole rotor system is stable, on the basis, when the thrust bearing contains a magnetic element, the magnetic element cannot tolerate high-temperature heat transmitted by a turbine, and a radial bearing is additionally arranged between the thrust bearing 700 and the turbine 200, so that the thrust bearing 700 is far away from the turbine 200 and is not influenced by high temperature, and the specific reference is made to fig. 35.
As shown in fig. 35, a vertical rotor system includes a rotating shaft 100, a turbine 200, a compressor 300, a motor 400, a first radial bearing 500, a second radial bearing 600, a thrust bearing 700, and a fourth radial bearing 801, the rotating shaft 100 passes through the first radial bearing 500, the motor 400, the compressor 300, the thrust bearing 700, the second radial bearing 600, the turbine 200, and the fourth radial bearing 801 which are sequentially arranged, the rotating shaft 100 rotates in the first radial bearing 500, the stator of the motor 400, the stator of the thrust bearing 700, the second radial bearing 600, and the fourth radial bearing 801, and the rotating shaft 100 is fixedly connected with a thrust disc of the thrust bearing 700, the turbine of the turbine 200, and a compression wheel of the compressor 300.
To improve the stability of the entire vertical rotor system, an improvement is made on the vertical rotor system of fig. 35, and a third radial bearing 800 is added between the motor 400 and the compressor 300, see fig. 36 in particular.
Preferably, the first radial bearing 500, the second radial bearing 600, the third radial bearing 800 and the fourth radial bearing 801 are all non-contact radial bearings.
Preferably, the second radial bearing 600 and the fourth radial bearing 801 are hybrid dynamic and static radial bearings combining a hydrostatic gas radial bearing and a hydrodynamic gas radial bearing.
Preferably, the first radial bearing 500 and the third radial bearing 800 are air-magnetic hybrid radial bearings.
Preferably, the motor 400 is a hydrodynamic bearing motor, and a portion of the rotating shaft 100 corresponding to the motor 400 is provided with a dynamic pressure generating groove.
Preferably, the end face of the turbine 200 adjacent to the second radial bearing 600 is provided with a thermally insulating material, such as aerogel.
Preferably, the compressor 300 is a centrifugal compressor.
Preferably, the turbine is a centrifugal turbine.
Preferably, when the first radial bearing 500, the second radial bearing 600, the third radial bearing 800 and the fourth radial bearing 801 are all non-contact radial bearings, when the rotating shaft 100 is not started, the rotating shaft 100 and the bearing sleeve 530 are concentrically arranged, after the rotating shaft 100 is started, the axis of the rotating shaft 100 deviates from any side of the axis of the bearing sleeve 530, and the eccentricity epsilon is 0.3 to 0.5, so as to ensure that a wedge-shaped gap can be formed between the bearing sleeve 530 and the rotating shaft 100, and when the rotating shaft rotates, gas is pressed into the wedge-shaped gap, so that pressure is generated to support a load. Eccentricity ratioWherein e is the distance between the axis of the rotating shaft and the axis of the bearing sleeve, R is the inner diameter of the bearing sleeve, R is the inner diameter of the rotating shaft, and R-R is the bearing clearance.
Preferably, on the basis that the second radial bearing 600 is a hybrid dynamic-static radial bearing combining a hydrostatic gas radial bearing and a hydrodynamic gas radial bearing, a magnetic element is added to form a hybrid gas-magnetic radial bearing, which has a structure substantially the same as that of the first radial bearing 500 and the third radial bearing 800 when they are hybrid gas-magnetic bearings, except that no magnetic element is disposed at a position of the second radial bearing 600 close to the turbine 200, because the magnetic element does not resist high temperature, and structural diagrams of a vertical rotor system in which the second radial bearing 600 is configured as a hybrid gas-magnetic radial bearing are shown in fig. 37 to 45, respectively, corresponding to fig. 28 to 36.
The horizontal rotor system and the vertical rotor system are both suitable for a gas turbine power generation combined unit, preferably a micro gas turbine power generation combined unit, wherein the micro gas turbine comprises a gas compressor (preferably a centrifugal gas compressor), a turbine (preferably a centrifugal turbine of the turbine 200), a combustion chamber (preferably an annular combustion chamber), a heat regenerator and the like.
The working process of the micro gas turbine power generation combined unit is as follows:
for the sake of convenience, a bearing that can perform a lubricating function without rotating a shaft is defined as a hydrostatic bearing, and a bearing that can operate only when the shaft rotates to a certain speed is defined as a hydrodynamic bearing. In the following description, the electromagnetic bearing and the hydrostatic gas bearing are collectively referred to as a hydrostatic bearing, and the hydrodynamic gas bearing is referred to as a hydrodynamic bearing.
S1: starting a bearing: the control system respectively starts the hydrostatic bearing parts in the radial bearing and the thrust bearing, so that the rotating shaft 100 is jacked up and suspended to a preset position, the thrust disc 701 reaches the preset position between the first stator 702 and the second stator 703, and a gap is reserved between the thrust disc and the end faces of the first stator 702 and the second stator 703;
s2: the micro gas turbine is started to work, air enters the centrifugal compressor through the air inlet channel, after being compressed, the air passes through the heat regenerator, and the compressed air at the outlet of the compressor 300 is preheated by high-temperature gas exhausted by the turbine of the turbine 200; the preheated air enters a combustion chamber to be mixed with fuel for combustion, the high-temperature and high-pressure gas after the full combustion in the combustion chamber impacts a turbine of the turbine 200 to rotate the turbine, the exhaust gas of the turbine enters a heat regenerator to preheat the airflow at the outlet of the gas compressor and then is discharged from a tail gas pipe, because the turbine is connected with the gas compressor, the turbine rotates to drive the gas compressor to rotate together and drag the front end generator to rotate to generate power and output shaft power, in the process, when the rotating speed of the rotating shaft 100 reaches a preset value, preferably 5% -30% of the rated rotating speed, the control system respectively controls the static pressure bearing parts in the radial bearing and the thrust bearing to stop working, when the rotating speed of the rotating shaft 100 exceeds a first-order critical speed or a second-order critical speed, the control system respectively controls the static pressure bearing parts of the radial bearing and the thrust bearing to start until the static pressure bearing parts stably exceed the critical speed, the control system controls the hydrostatic bearing portions of the radial bearing and the thrust bearing to stop working respectively.
S3: stopping the micro gas turbine, gradually reducing the rotating speed of the rotating shaft 100, when the rotating speed of the rotating shaft 100 passes a first-order critical speed or a second-order critical speed, respectively controlling the static pressure bearing parts of the radial bearing and the thrust bearing to start by the control system, and respectively controlling the static pressure bearing parts of the radial bearing and the thrust bearing to stop working until the stability passes the critical speed; when the rotating speed of the rotating shaft 100 is reduced to a preset value, preferably, when the rotating speed is 5% -30% of the rated rotating speed, the control system respectively controls the static pressure bearing parts of the radial bearing and the thrust bearing to start until the rotating speed is reduced to 0, and then the control system respectively controls the static pressure bearing parts of the radial bearing and the thrust bearing to stop working.
Preferably, in step S1, the air intake duct is composed of a casing of the generator and a casing of the micro gas turbine, and the air cools the generator during entering the centrifugal compressor from the air intake duct.
Preferably, the compressor 300 includes blades and vanes, more preferably, the vanes are diffusers, and in step S2: the process that air enters the centrifugal compressor from the air inlet channel and is compressed is as follows: the air enters the centrifugal compressor moving blades, is compressed and then enters a diffuser (a static part) arranged in the circumferential direction to be continuously compressed.
Preferably, the turbine of the turbine 200 includes vanes and blades, more preferably, the vanes are nozzles, and the step of "the high-temperature and high-pressure gas fully combusted in the combustion chamber collides with the turbine of the turbine 200 and rotates the turbine" in step S2 includes: after the high-temperature and high-pressure gas fully combusted in the combustion chamber is expanded and accelerated through a nozzle (a static part) circumferentially arranged at the outlet of the combustion chamber, the high-temperature and high-pressure gas impacts turbine movable blades (namely, the gas is continuously expanded and works on the turbine), so that the turbine rotates.
The above embodiments are only specific embodiments of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art can easily think of changes or substitutions within the technical scope of the present invention, and all should be covered within the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.
Claims (13)
1. A bearing damper for mounting in a non-contact bearing, the bearing damper being made of a shape memory material, the bearing damper being capable of adjusting a bearing clearance between a stationary member and a rotating member by plastic deformation.
2. The bearing damper of claim 1, wherein the bearing damper comprises at least two adjustment units;
the bearing damper is an integral device formed by continuously arranging the at least two adjusting units; or,
the bearing damper comprises at least two independently arranged adjustment members, which comprise at least one of the adjustment units.
3. The bearing damper as recited in claim 2, wherein the adjustment unit is a half shell structure including a boss and a support, the boss being integrally formed with the support.
4. A radial bearing, characterized in that it comprises:
a bearing body;
the bearing inner ring is sleeved in the bearing body, and a bearing gap is formed between the bearing inner ring and a rotating shaft sleeved in the bearing inner ring;
and the bearing damper according to any one of claims 1 to 3, which is provided between the bearing inner ring and the bearing body, and which is capable of being plastically deformed by the bearing inner ring to adjust the bearing gap.
5. The radial bearing according to claim 4, wherein the adjustment unit of the bearing damper is a half-shell structure;
the convex part of the bearing damper faces the bearing inner ring, and the supporting part of the bearing damper is attached to the inner diameter surface of the bearing body;
the convex part can be subjected to plastic deformation under the action of the bearing inner ring so as to adjust the bearing clearance.
6. The radial bearing of claim 4 wherein said bearing damper comprises at least two independently disposed adjustment members;
the adjusting components are uniformly distributed along the circumferential direction of the inner diameter surface of the bearing body; and/or the presence of a gas in the gas,
the adjusting components are axially and uniformly distributed along the inner diameter surface of the bearing body.
7. The radial bearing according to claim 4, wherein a dynamic pressure generating groove is provided on an inner diameter surface of the inner race or a circumferential surface of the rotating shaft facing the inner race;
and/or the presence of a gas in the gas,
the radial bearing is provided with a static pressure air inlet throttling hole which is communicated with the bearing gap and an external air source, and the static pressure air inlet throttling hole is used for conveying the external air source into the bearing gap;
and/or the presence of a gas in the gas,
the bearing body is provided with a plurality of magnetic components, and the rotating shaft can move in the radial direction of the rotating shaft under the action of the magnetic force of the magnetic components.
8. A thrust bearing for mounting on a rotating shaft, the thrust bearing comprising:
the thrust disc is connected to the rotating shaft;
the first stator and the second stator are arranged on the rotating shaft in a penetrating mode and are respectively arranged on two opposite sides of the thrust disc;
each of the first stator and the second stator comprises a stator body, a pressure plate and the bearing damper of any one of claims 1 to 3, the bearing damper is arranged between the stator body and the pressure plate, the pressure plate is arranged on one side of the stator body close to the thrust disc, and a bearing gap is arranged between the pressure plate and the thrust disc;
wherein the bearing damper is capable of undergoing plastic deformation under the action of the pressure plate to adjust the bearing clearance.
9. The thrust bearing of claim 8, wherein the adjustment unit of the bearing damper is a half-shell structure;
the convex part of the bearing damper faces the pressure plate, and the supporting part of the bearing damper is attached to the stator body;
the convex part can be subjected to plastic deformation under the action of the pressure plate so as to adjust the bearing clearance.
10. A thrust bearing according to claim 8, wherein the bearing damper comprises at least two independently disposed adjustment members;
the adjusting components are uniformly distributed along the circumferential direction of the end surface of the stator body; and/or the presence of a gas in the gas,
the adjusting components are uniformly distributed along the radial direction of the end face of the stator body.
11. The thrust bearing of claim 8, wherein a dynamic pressure generating groove is provided on an end surface of the pressure plate facing the thrust disk or an end surface of the thrust disk facing the pressure plate;
and/or the presence of a gas in the gas,
in the first stator and the second stator, each stator is also provided with a static pressure air inlet orifice for communicating the bearing gap with an external air source, and the static pressure air inlet orifice is used for conveying the external air source into the bearing gap;
and/or the presence of a gas in the gas,
the thrust disc is provided with a first magnetic component, the stator body is further provided with a plurality of second magnetic components, and the thrust disc can move in the axial direction of the rotating shaft under the action of magnetic force between the first magnetic component and the second magnetic components.
12. A rotor system is characterized by comprising a rotating shaft, a thrust bearing and at least two radial bearings, wherein the thrust bearing and the at least two radial bearings are both arranged on the rotating shaft, and the thrust bearing and the at least two radial bearings are both non-contact bearings;
wherein at least one of the at least two radial bearings is the radial bearing of any one of claims 4 to 7; and/or the thrust bearing is the thrust bearing of any one of claims 8 to 11.
13. The rotor system of claim 12,
the shaft body of the rotating shaft is of an integrated structure, and the rotating shaft is horizontally arranged or vertically arranged;
the rotating shaft is also sequentially provided with a motor, a gas compressor and a turbine;
the thrust bearing is arranged at a preset position on one side of the turbine close to the compressor, and the preset position is a position which can enable the gravity center of the rotor system to be located between two radial bearings which are farthest away from each other in the at least two radial bearings.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821612816.XU CN208858777U (en) | 2018-09-30 | 2018-09-30 | A kind of bearing damp device, transverse bearing, thrust bearing and rotor-support-foundation system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201821612816.XU CN208858777U (en) | 2018-09-30 | 2018-09-30 | A kind of bearing damp device, transverse bearing, thrust bearing and rotor-support-foundation system |
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| CN208858777U true CN208858777U (en) | 2019-05-14 |
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| CN201821612816.XU Active CN208858777U (en) | 2018-09-30 | 2018-09-30 | A kind of bearing damp device, transverse bearing, thrust bearing and rotor-support-foundation system |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110243601A (en) * | 2019-07-08 | 2019-09-17 | 淮海工学院 | A combined thrust and radial bearing device suitable for ultra-high-speed working conditions and its detection method |
| CN110966305A (en) * | 2018-09-30 | 2020-04-07 | 至玥腾风科技投资集团有限公司 | Bearing damper, radial bearing, thrust bearing and rotor system |
| CN111288082A (en) * | 2019-12-11 | 2020-06-16 | 燕山大学 | Control system of single-degree-of-freedom magnetic-liquid double-suspension bearing |
| CN111288081A (en) * | 2019-12-11 | 2020-06-16 | 燕山大学 | Single-degree-of-freedom magnetic-liquid double-suspension bearing control system |
| CN111350757A (en) * | 2019-12-11 | 2020-06-30 | 燕山大学 | Single-degree-of-freedom magnetic-liquid double-suspension bearing control method |
| WO2021143415A1 (en) * | 2020-01-19 | 2021-07-22 | 至玥腾风科技集团有限公司 | Air bearing comprising adaptive damper |
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2018
- 2018-09-30 CN CN201821612816.XU patent/CN208858777U/en active Active
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110966305A (en) * | 2018-09-30 | 2020-04-07 | 至玥腾风科技投资集团有限公司 | Bearing damper, radial bearing, thrust bearing and rotor system |
| CN110243601A (en) * | 2019-07-08 | 2019-09-17 | 淮海工学院 | A combined thrust and radial bearing device suitable for ultra-high-speed working conditions and its detection method |
| CN110243601B (en) * | 2019-07-08 | 2020-10-09 | 淮海工学院 | A combined thrust and radial bearing device suitable for ultra-high speed conditions and its detection method |
| CN111288082A (en) * | 2019-12-11 | 2020-06-16 | 燕山大学 | Control system of single-degree-of-freedom magnetic-liquid double-suspension bearing |
| CN111288081A (en) * | 2019-12-11 | 2020-06-16 | 燕山大学 | Single-degree-of-freedom magnetic-liquid double-suspension bearing control system |
| CN111350757A (en) * | 2019-12-11 | 2020-06-30 | 燕山大学 | Single-degree-of-freedom magnetic-liquid double-suspension bearing control method |
| CN111350757B (en) * | 2019-12-11 | 2021-12-21 | 燕山大学 | A single-degree-of-freedom magnetic-hydraulic double-suspended bearing control method |
| CN111288081B (en) * | 2019-12-11 | 2022-03-11 | 燕山大学 | A single-degree-of-freedom magnetic-hydraulic double-suspended bearing control system |
| WO2021143415A1 (en) * | 2020-01-19 | 2021-07-22 | 至玥腾风科技集团有限公司 | Air bearing comprising adaptive damper |
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