Integrated sensing and actuating active control intelligent hybrid dynamic and static pressure sliding bearing

Abstract

The application discloses an integrated perception and execution active control intelligent dynamic and static pressure hybrid sliding bearing, and belongs to the technical field of hybrid sliding bearings. In order to solve the problem that the existing dynamic and static pressure hybrid sliding bearing has no good active compensation ability when the working condition of the dynamic and static pressure hybrid sliding bearing changes (such as sudden load, fluctuating load and other unstable working conditions), the application comprises an outer shell, an intermediate shell, a bearing body, an X-direction servo valve, a Y-direction servo valve and a servo valve control system. The outer shell is sleeved on the intermediate shell, and the intermediate shell is sleeved on the bearing body. The X-direction servo valve and the Y-direction servo valve are both installed on the outer circumferential surface of the outer shell. The signal input end of the servo valve control system is installed on the outer shell. The signal output end of the servo valve control system is connected with the control end of the X-direction servo valve and the control end of the Y-direction servo valve through wires. High-pressure oil liquid passes through the X-direction servo valve and the Y-direction servo valve, and then passes through the outer shell and the intermediate shell in sequence, and finally enters the bearing body and the shaft system to form an active oil film. The application is mainly used as a supporting bearing structure in large rotating machinery.

Description

Technical Field

[0001] The present invention belongs to the technical field of hybrid sliding bearings, and in particular relates to an actively controlled intelligent dynamic and static pressure hybrid sliding bearing with integrated sensing and execution. Background Art

[0002] Large rotating machinery is widely used in industrial and aerospace mechanical devices, such as aircraft engines and gas turbines. Large rotating machinery is also one of the key equipment in the basic industries and facilities of a few countries. Sliding bearings are its main supporting components, and the characteristics of the bearings have a great impact on the performance of its system. Dynamic and static pressure sliding bearings have strong stability and can work stably within a large load range. However, dynamic and static pressure hybrid sliding bearings are passive components during use. When the working conditions change (such as sudden loads, fluctuating loads and other unstable working conditions), they do not have good active compensation capabilities, which can easily affect the working stability of the dynamic and static pressure hybrid sliding bearings. Therefore, in order to overcome the above problems, it is very practical to develop an active control intelligent dynamic and static pressure hybrid sliding bearing that integrates perception and execution. Summary of the Invention

[0003] To address the drawback of existing dynamic-static hybrid sliding bearings that lack active compensation capabilities when operating conditions change (e.g., sudden loads, fluctuating loads, and other unstable operating conditions), the present invention provides an actively controlled intelligent dynamic-static hybrid sliding bearing with integrated sensing and execution.

[0004] An actively controlled intelligent dynamic and static pressure hybrid sliding bearing with integrated sensing and execution, the dynamic and static pressure hybrid sliding bearing comprising an outer shell, an intermediate shell, a bearing body, an X-direction servo valve, a Y-direction servo valve, and a servo valve control system. The outer shell is sleeved on the intermediate shell, which is sleeved on the bearing body, and the outer shell, intermediate shell, and bearing body are coaxially arranged. The X-direction servo valve and the Y-direction servo valve are both mounted on the outer circumferential surface of the outer shell, and the X-direction servo valve is offset 90 degrees relative to the Y-direction servo valve. The signal input end of the servo valve control system is mounted on the outer shell, and the signal output end of the servo valve control system is connected to the control end of the X-direction servo valve and the control end of the Y-direction servo valve via a wire. High-pressure oil passes through the X-direction servo valve and the Y-direction servo valve and, in sequence, through the outer shell and the intermediate shell, ultimately enters between the bearing body and the shafting to form an active oil film. The servo valve control system is used to control the operating states of the X-direction servo valve and the Y-direction servo valve.

[0005] Further, the servo valve control system comprises an X-direction sensor, a Y-direction sensor, a controller and an electro-hydraulic servo driver, the X-direction sensor and the Y-direction sensor are both fixed on an end face of the outer shell through a sensor mounting bracket, the X-direction sensor is arranged corresponding to the X-direction servo valve, and the Y-direction sensor is arranged corresponding to the Y-direction servo valve, the controller and the electro-hydraulic servo driver are both arranged outside the outer shell, the signal output end of the X-direction sensor and the signal output end of the Y-direction sensor are both connected with the signal input end of the controller through wires, the signal output end of the controller is connected with the signal input end of the electro-hydraulic servo driver through wires, and the signal output end of the electro-hydraulic servo driver is connected with the control end of the X-direction servo valve and the control end of the Y-direction servo valve through wires respectively;

[0006] Further, two oil supply hole groups are arranged on the outer circular face of the outer shell, one oil supply hole group is arranged corresponding to the X-direction servo valve, and the other oil supply hole group is arranged corresponding to the Y-direction servo valve, each oil supply hole group comprises a servo valve A end oil supply hole and a servo valve B end oil supply hole, and the servo valve A end oil supply hole and the servo valve B end oil supply hole of each group are in communication with the oil outlet end of the corresponding X-direction servo valve or the oil outlet end of the Y-direction servo valve, and two outer shell oil groove groups are arranged on the inner circular face of the outer shell, each outer shell oil groove group is arranged corresponding to an oil supply hole group, and each outer shell oil groove group comprises two outer shell oil grooves, one outer shell oil groove is in communication with the servo valve A end oil supply hole in the corresponding oil supply hole group, and the other outer shell oil groove is in communication with the servo valve B end oil supply hole in the corresponding oil supply hole group.

[0007] Further, an X-direction servo valve connecting seat is arranged on the outer shell corresponding to the X-direction servo valve, the X-direction servo valve is mounted on the X-direction servo valve connecting seat, an X-direction high-pressure oil supply hole is arranged on the X-direction servo valve connecting seat, the oil inlet end of the X-direction servo valve is connected with a first oil outlet pipe of a high-pressure oil supply mechanism through the X-direction high-pressure oil supply hole, the oil outlet end of the X-direction servo valve is connected with the servo valve A end oil supply hole and the servo valve B end oil supply hole corresponding thereto, a Y-direction servo valve connecting seat is arranged on the outer shell corresponding to the Y-direction servo valve, the Y-direction servo valve is mounted on the Y-direction servo valve connecting seat, a Y-direction high-pressure oil supply hole is arranged on the Y-direction servo valve connecting seat, the oil inlet end of the Y-direction servo valve is connected with a second oil outlet pipe of the high-pressure oil supply mechanism through the Y-direction high-pressure oil supply hole, and the oil outlet end of the Y-direction servo valve is connected with the servo valve A end oil supply hole and the servo valve B end oil supply hole corresponding thereto.

[0008] Furthermore, two inner shell oil groove groups are machined on the outer circumferential surface of the intermediate shell, each inner shell oil groove group is correspondingly arranged with an outer shell oil groove group, each inner shell oil groove group includes two inner shell oil grooves, each inner shell oil groove is correspondingly arranged with an outer shell oil groove, each inner shell oil groove and the corresponding outer shell oil groove are assembled into a complete arc-shaped oil cavity, and a transfer oil supply hole is machined at the bottom of the inner shell oil groove, and each transfer oil supply hole and the servo valve A end oil supply hole or the servo valve B end oil supply hole located in the same arc-shaped oil cavity are respectively arranged at both ends of the arc-shaped oil cavity;

[0009] Furthermore, two oil return ring grooves are symmetrically processed on the inner ring surface of the bearing body along the center line of the bearing body thickness direction, and a plurality of inner oil grooves are equidistantly processed along the inner circumference of the bearing body between the two oil return ring grooves, and the two ends of each inner oil groove are respectively connected to an oil return ring groove, and an inner wall surface is formed between the two adjacent inner oil grooves, and a plurality of bearing body high-pressure oil supply hole groups are equidistantly processed along the circumferential direction on the outer circular surface of the bearing body, each bearing body high-pressure oil supply hole group is corresponding to an inner wall surface, and a plurality of high-pressure oil hole systems are equidistantly processed inside the bearing body along the circumferential direction, and each high-pressure oil hole system is located between a bearing body high-pressure oil supply hole group and an inner wall surface, one end of each high-pressure oil hole system is connected to the bearing body high-pressure oil supply hole group, and the other end of each high-pressure oil hole system is connected to the inner wall surface;

[0010] Furthermore, the bearing body high-pressure oil supply hole group includes two high-pressure oil holes (21), and the two high-pressure oil holes (21) in the same group are symmetrically arranged along the center line of the width direction of the bearing body (3), and one high-pressure oil hole (21) in each bearing body high-pressure oil supply hole group is arranged corresponding to the corresponding arc-shaped oil cavity, and the high-pressure oil hole system (12) includes two oil inlet ends and three oil outlet ends, each oil inlet end of the high-pressure oil hole system (12) is connected to a high-pressure oil hole (21) and each oil outlet end of the high-pressure oil hole system (12) is connected to the inner wall surface (10);

[0011] Furthermore, the number of the inner oil grooves is an even number;

[0012] Furthermore, the inner wall surface is uniformly processed with a plurality of micro textures;

[0013] Furthermore, a low-pressure oil hole for the outer shell is machined on the outer circumferential surface of the outer shell, a low-pressure oil hole for the inner shell is machined on the outer circumferential surface of the intermediate shell, and a low-pressure oil supply ring groove is machined on the outer circumferential surface of the bearing body. One end of the low-pressure oil hole of the outer shell is connected to the oil outlet pipe of the high-pressure oil supply mechanism, and the other end of the low-pressure oil hole of the outer shell is connected to one end of the low-pressure oil hole of the inner shell, and the other end of the low-pressure oil hole of the inner shell is connected to the low-pressure oil supply ring groove. A plurality of low-pressure oil holes are machined on the bottom of the low-pressure oil supply ring groove at equal intervals along the circumferential direction, and each low-pressure oil hole is correspondingly arranged between an inner oil groove and the low-pressure oil supply ring groove, and one end of each low-pressure oil hole is connected to the low-pressure oil supply ring groove, and the other end of each low-pressure oil hole is connected to the corresponding inner oil groove;

[0014] The beneficial effects of this application compared to the prior art are as follows:

[0015] This application proposes an intelligent, actively controlled, dynamic and static hybrid sliding bearing with integrated sensing and execution. By connecting the oil circuits between the intermediate housing and the oil tank within the outer housing, this simplifies the installation process of the bearing and servo valve, expanding the bearing's application range. Furthermore, the dynamic and static hybrid sliding bearing provided in this application also has uniformly arranged micro-textures on its inner wall surface to increase the bearing's load capacity, stiffness, and damping, thereby improving the bearing's stability.

[0016] The present application proposes an integrated sensing and execution active control intelligent dynamic and static pressure hybrid sliding bearing. The inner wall surface is provided with an array of high-pressure oil supply holes. By connecting to an external oil source, a static pressure effect is achieved, thereby improving the bearing's load-bearing capacity. Compared with traditional dynamic and static pressure hybrid sliding bearings, the present application provides a servo valve on the outer shell of the dynamic and static pressure hybrid sliding bearing. By connecting to the servo valve control system, the sensing and actuator mechanisms are integrated to generate a controllable active oil film force. The appropriate active oil film force is generated based on the shaft center position feedback, reducing the vibration amplitude of the rotor, thereby improving the stability of the bearing.

[0017] The present application proposes an integrated sensing and execution active control intelligent dynamic and static pressure hybrid sliding bearing which can still be used as a passive device with high stability in the absence of active control and has a wide range of applications. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 Schematic diagram of the three-dimensional structure of the active control intelligent dynamic and static pressure hybrid sliding bearing with integrated perception and execution described in this application;

[0019] Figure 2 A top view of the active control intelligent dynamic and static pressure hybrid sliding bearing with integrated sensing and execution as described in this application;

[0020] Figure 3 A side view of the active control intelligent dynamic and static hybrid sliding bearing with integrated sensing and execution as described in this application;

[0021] Figure 4 AA schematic diagram of the active control intelligent dynamic and static pressure hybrid sliding bearing with integrated perception and execution described in this application;

[0022] Figure 5 This is a BB-direction schematic diagram of the active control intelligent dynamic and static pressure hybrid sliding bearing with integrated perception and execution described in this application;

[0023] Figure 6 A three-dimensional schematic diagram of the bearing body in the active control intelligent dynamic and static pressure hybrid sliding bearing with integrated sensing and execution described in this application;

[0024] Figure 7 This is a schematic diagram of the main view of the bearing body in the active control intelligent dynamic and static pressure hybrid sliding bearing with integrated perception and execution described in this application;

[0025] Figure 8 This is a DD-direction view of the bearing body in the active control intelligent dynamic and static pressure hybrid sliding bearing with integrated perception and execution described in this application;

[0026] Figure 9 This is an EE view of the bearing body in the active control intelligent dynamic and static pressure hybrid sliding bearing with integrated perception and execution described in this application;

[0027] Figure 10 This is a side view of the bearing body in the active control intelligent dynamic and static pressure hybrid sliding bearing with integrated perception and execution described in this application:

[0028] Figure 11 A CC-direction schematic diagram of a bearing body in an active-controlled intelligent dynamic-static hybrid sliding bearing with integrated sensing and execution as described in this application;

[0029] Figure 12 A three-dimensional schematic diagram of the intermediate housing in the active control intelligent dynamic and static hybrid sliding bearing with integrated sensing and execution described in this application;

[0030] Figure 13 A left-side schematic diagram of the intermediate housing in the active control intelligent dynamic and static hybrid sliding bearing with integrated sensing and execution described in this application;

[0031] Figure 14 A three-dimensional schematic diagram of the outer shell of the active control intelligent dynamic and static hybrid sliding bearing with integrated sensing and execution described in this application;

[0032] Figure 15 A side cross-sectional diagram of the outer shell of the active control intelligent dynamic and static pressure hybrid sliding bearing with integrated sensing and execution described in this application;

[0033] Figure 16A schematic diagram of the bearing body wall surface in the active control intelligent dynamic and static pressure hybrid sliding bearing with integrated sensing and execution as described in this application;

[0034] Figure 17 This is a control block diagram of the active control intelligent dynamic and static hybrid sliding bearing with integrated perception and execution as described in this application;

[0035] Figure 18 This is a flowchart of the vibrator working process of the active control intelligent dynamic and static pressure hybrid sliding bearing with integrated perception and execution described in this application;

[0036] In the figure, 1 is the outer shell, 2 is the intermediate shell, 3 is the bearing body, 4 is the X-direction servo valve, 5 is the X-direction high-pressure oil supply hole, 6 is the Y-direction servo valve, 7 is the Y-direction high-pressure oil supply hole, 8 is the low-pressure oil hole, 9 is the inner oil groove, 10 is the inner wall, 11 is the X-direction sensor, 12 is the high-pressure oil hole system, 13 is the Y-direction sensor, 14 is the controller, 15 is the electro-hydraulic servo driver, 16 is the servo valve A-end oil supply hole, 17 is the servo valve B-end oil supply hole, 18 is the outer shell oil groove, 19 is the inner shell oil groove, 20 is the adapter oil supply hole, 21, 22 is the outer shell low-pressure oil hole, 23 is the inner shell low-pressure oil hole, 24 is the low-pressure oil supply ring groove, 25 is the oil return ring groove, 26 is the sealing ring groove and 27 is the micro-texture. DETAILED DESCRIPTION

[0037] Specific implementation method 1: Combination Figures 1 to 18 This embodiment describes an actively controlled intelligent dynamic and static hybrid sliding bearing with integrated sensing and execution. The dynamic and static hybrid sliding bearing includes an outer shell 1, an intermediate shell 2, a bearing body 3, an X-direction servo valve 4, a Y-direction servo valve 6, and a servo valve control system. The outer shell 1 is mounted on the intermediate shell 2, which is mounted on the bearing body 3. The outer shell 1, intermediate shell 2, and bearing body 3 are coaxially arranged. The X-direction servo valve 4 and the Y-direction servo valve 6 are both mounted on the outer circumferential surface of the outer shell 1, and the X-direction servo valve 4 is offset 90 degrees relative to the Y-direction servo valve 6. The signal input end of the servo valve control system is mounted on the outer shell 1, and the signal output end of the servo valve control system is connected to the control end of the X-direction servo valve 4 and the control end of the Y-direction servo valve 6 via a wire. High-pressure oil passes through the X-direction servo valve 4 and the Y-direction servo valve 6 and then passes through the outer shell 1 and the intermediate shell 2 in sequence, finally entering between the bearing body 3 and the shafting to form an active oil film. The servo valve control system is used to control the operating status of the X-direction servo valve 4 and the Y-direction servo valve 6.

[0038] The integrated sensing and executing active control intelligent hybrid dynamic and static pressure sliding bearing provided in the embodiment is further optimized on the basis of the hybrid dynamic and static pressure sliding bearing, the oil supply hole is connected with the external oil source and the injection flow is controlled through the servo valve, the oil film pressure distribution is further changed, the active oil film force is generated and the dynamic characteristics of the bearing are changed, the rotor motion state can be monitored in real time through the feedback signal of the sensor, the control algorithm and parameters can be adjusted based on different purposes to obtain the best control; when the bearing is used as a passive control device, the bearing has the advantage of high bearing capacity of the sliding bearing, and when active control is performed, the bearing-rotor system can be compensated through the active oil film force to further reduce the rotor vibration; when the active control is not performed, the control program is used to make the controller generate a periodic sine signal or a step signal to make the bearing generate a liquid excitation force, so that the bearing can be used as an exciter to expand the application range of the bearing.

[0039] Specific embodiment two: combination Figures 1 to 18 In the embodiment, the difference between the embodiment and the specific embodiment one is that the servo valve control system comprises an X-direction sensor 11, a Y-direction sensor 13, a controller 14 and an electro-hydraulic servo driver 15, the X-direction sensor 11 and the Y-direction sensor 13 are both fixed on one end face of the outer shell 1 through a sensor mounting bracket, the X-direction sensor 11 is arranged corresponding to the X-direction servo valve 4, and the Y-direction sensor 13 is arranged corresponding to the Y-direction servo valve 6, the controller 14 and the electro-hydraulic servo driver 15 are both arranged outside the outer shell 1, the signal output end of the X-direction sensor 11 and the signal output end of the Y-direction sensor 13 are both connected with the signal input end of the controller 14 through wires, the signal output end of the controller 14 is connected with the signal input end of the electro-hydraulic servo driver 15 through a wire, and the signal output end of the electro-hydraulic servo driver 15 is connected with the control end of the X-direction servo valve 4 and the control end of the Y-direction servo valve 6 through wires respectively. The other components and connection modes are the same as those in the specific embodiment one.

[0040] In the embodiment, the sensor structure arranged in two perpendicular directions is used to measure the shaft center displacement or acceleration of the rotor at the bearing position, when the feedback control is performed, the sensor feeds back the measured rotor displacement or acceleration voltage signal to the controller for calculation of the control signal, since a high-frequency control signal is required to control the servo valve, the FPGA / ARM controller is adopted to output a high-frequency control signal, the controller calculates the control amount through the control algorithm, outputs the control signal and transmits it to the electro-hydraulic servo driver, and converts the voltage signal into a current signal in the working range of the servo valve, thereby controlling the flow injected into the bearing oil film, completing the feedback control, generating a controllable active oil film force, compensating for the changes of the rotor operating conditions, and equivalent to increasing the bearing capacity, stiffness and damping of the bearing.

[0041] The actively controlled intelligent dynamic and static pressure hybrid sliding bearing provided in this application can also be used as a hydraulic exciter. By inputting a periodic voltage signal to the servo valve in the program setting, the bearing generates a periodic excitation force, and the vibration displacement response of the component is obtained through the displacement / acceleration sensor, thereby analyzing the excitation characteristics of the component in real time.

[0042] Specific implementation method three: Combination Figures 1 to 18 This embodiment differs from the second embodiment in that two oil supply hole groups are provided on the outer circumference of the outer shell 1. One oil supply hole group corresponds to the X-direction servo valve 4, and the other oil supply hole group corresponds to the Y-direction servo valve 6. Each oil supply hole group includes an oil supply hole 16 at the servo valve A end and an oil supply hole 17 at the servo valve B end. Each group of servo valve A end oil supply hole 16 and servo valve B end oil supply hole 17 is connected to the oil outlet of the corresponding X-direction servo valve 4 or Y-direction servo valve 6. Two housing oil groove groups are machined on the inner circumference of the outer shell 1. Each housing oil groove group corresponds to an oil supply hole group. Each housing oil groove group includes two housing oil grooves 18: one housing oil groove 18 is connected to the oil supply hole 16 at the servo valve A end of the corresponding oil supply hole group, and the other housing oil groove 18 is connected to the oil supply hole 17 at the servo valve B end of the corresponding oil supply hole group. Other components and connection methods are the same as those of the second embodiment.

[0043] Specific implementation method four: Combination Figures 1 to 18 To explain this embodiment, the difference between this embodiment and the specific embodiment three is that an X-direction servo valve connecting seat is provided on the outer shell 1 at a position corresponding to the X-direction servo valve 4, the X-direction servo valve 4 is installed on the X-direction servo valve connecting seat, and an X-direction high-pressure oil supply hole 5 is provided on the X-direction servo valve connecting seat. The oil inlet end of the X-direction servo valve 4 is connected to the No. 1 oil outlet pipe of the high-pressure oil supply mechanism through the X-direction high-pressure oil supply hole 5, and the oil outlet end of the X-direction servo valve 4 is connected to the corresponding servo valve A end oil supply hole 16 and servo valve B end oil supply hole 17. A Y-direction servo valve connecting seat is provided on the outer shell 1 at a position corresponding to the Y-direction servo valve 6, the Y-direction servo valve 6 is installed on the Y-direction servo valve connecting seat, and a Y-direction high-pressure oil supply hole 7 is provided on the Y-direction servo valve connecting seat. The oil inlet end of the Y-direction servo valve 6 is connected to the No. 2 oil outlet pipe of the high-pressure oil supply mechanism through the Y-direction high-pressure oil supply hole 7, and the oil outlet end of the Y-direction servo valve 6 is connected to the corresponding servo valve A end oil supply hole 16 and servo valve B end oil supply hole 17. Other components and connection methods are the same as those in the third embodiment.

[0044] Specific implementation method five: Combination Figures 1 to 18The difference between the embodiment and the fourth embodiment is that the outer circumferential surface of the intermediate shell 2 is machined with two inner shell oil groove groups, each of which is arranged correspondingly to an outer shell oil groove group, each of which includes two inner shell oil grooves 19, each of which is arranged correspondingly to an outer shell oil groove 18, each of which is combined with the corresponding outer shell oil groove 18 to form a complete arc-shaped oil cavity, the bottom of each inner shell oil groove 19 is machined with a switching oil supply hole 20, and each switching oil supply hole 20 is arranged at the two ends of the arc-shaped oil cavity with the servo valve A end oil supply hole 16 or the servo valve B end oil supply hole 17 in the same arc-shaped oil cavity. The other components and connection modes are the same as those of the fourth embodiment.

[0045] The sixth embodiment is as follows: Figures 1 to 18 The difference between the embodiment and the fifth embodiment is that the inner annular surface of the bearing body 3 is machined with two oil return ring grooves 25 along the centerline of the thickness direction of the bearing body 3, multiple inner side oil grooves 9 are machined equidistantly along the inner periphery of the bearing body 3 between the two oil return ring grooves 25, and the two ends of each inner side oil groove 9 are arranged correspondingly to an oil return ring groove 25, the inner race surface 10 is formed between adjacent two inner side oil grooves 9, multiple bearing body high-pressure oil supply hole groups are machined equidistantly along the circumference on the outer circumferential surface of the bearing body 3, each of which is arranged correspondingly to an inner race surface 10, multiple high-pressure oil hole systems 12 are machined equidistantly along the circumference inside the bearing body 3, each of which is located between a bearing body high-pressure oil supply hole group and an inner race surface 10, one end of each high-pressure oil hole system 12 is arranged correspondingly to the bearing body high-pressure oil supply hole group, and the other end of each high-pressure oil hole system 12 is arranged correspondingly to the inner race surface 10. The other components and connection modes are the same as those of the fifth embodiment.

[0046] As described in Embodiment Three to Embodiment Seven, the X-direction servo valve 4 and the Y-direction servo valve 6 are identical in structure, each of which is connected to a corresponding set of alignment oil supply holes on the bearing for controlling the vibration of the rotor in two perpendicular directions. Each servo valve has four oil passage interfaces, one of which is connected to a high-pressure oil station for high-pressure oil supply, one is a return oil interface which is sealed and not used for return oil, and the remaining two are oil supply interfaces. Two oil supply interfaces on each servo valve are connected to a corresponding set of alignment oil supply holes on the outer shell 1. The outer shell 1 and the intermediate shell 2 form a plurality of arc-shaped oil chambers therebetween, each of which is connected to a corresponding servo valve A end oil supply hole 16 or a servo valve B end oil supply hole 17. The servo valve A end oil supply hole 16 or the servo valve B end oil supply hole 17 is arranged at one end of the arc-shaped oil chamber. The other end of each arc-shaped oil chamber is connected to a corresponding transfer oil supply hole 20. Two transfer oil supply holes 20 in the same set of arc-shaped oil chambers are symmetrically arranged around the bearing center. When the lubricating oil flows from the outer shell 1 into the intermediate shell 2, it enters the bearing body 3 through the servo valve A end oil supply hole 16 or the servo valve B end oil supply hole 17 and then enters the bearing body 3 through the transfer oil supply hole 20. The bearing body 3 is provided with a plurality of high-pressure oil hole systems 12 and a plurality of bearing body high-pressure oil supply hole sets. Each high-pressure oil hole system 12 and a corresponding bearing body high-pressure oil supply hole set form a high-pressure oil passage to guide the high-pressure oil in the bearing body 3 to the space between the bearing body 3 and the rotor to form an oil film. It is worth noting that the plurality of high-pressure oil hole systems 12 are equidistantly arranged along the circumference of the bearing body 3, and each high-pressure oil hole system 12 is arranged corresponding to an inner raceway 10 in the bearing body 3 to ensure that the oil supply pressure of each high-pressure oil supply hole on a single raceway is consistent. The plurality of arc-shaped oil chambers serve as transfer oil passages of the bearing body, eliminating the need for additional oil passages to connect the servo valve and the bearing body, simplifying the installation of the bearing, and combining Figures 12 to 14 It is worth noting that the inner side of the outer shell 1 is equidistantly provided with a plurality of sealing ring grooves 26 along the axial direction of the outer shell 1. The outer ring surface of the intermediate shell 2 is also provided with a half-ring groove structure corresponding to the half-ring groove structure of the sealing ring groove 26. The two structures are combined to form a complete sealing ring. When high-pressure oil enters the arc-shaped oil chamber, the high-pressure oil enters the sealing ring through the gap between the outer shell oil groove 18 and the inner shell oil groove 19 for oil sealing. Figures 1 to 3 As shown in FIG. 6, the X-direction servo valve 4 and the Y-direction servo valve 6 are offset and misaligned. The purpose is to ensure the stability of the arrangement of the X-direction servo valve 4 and the Y-direction servo valve 6 and to avoid interference between the corresponding oil passages. The return oil in the bearing finally enters the return oil groove 25 and flows out to the outside of the bearing through the gap.

[0047] Embodiment Seven: As shown in FIG. 6, the X-direction servo valve 4 and the Y-direction servo valve 6 are offset and misaligned. The purpose is to ensure the stability of the arrangement of the X-direction servo valve 4 and the Y-direction servo valve 6 and to avoid interference between the corresponding oil passages. The return oil in the bearing finally enters the return oil groove 25 and flows out to the outside of the bearing through the gap. Figures 1 to 18This embodiment is described. This embodiment differs from Specific Embodiment 6 in that the bearing body high-pressure oil supply hole group includes two high-pressure oil holes 21. The two high-pressure oil holes 21 in the same group are symmetrically arranged along the centerline of the width direction of the bearing body 3. In addition, one high-pressure oil hole 21 in each bearing body high-pressure oil supply hole group is corresponding to the corresponding arc-shaped oil cavity. The high-pressure oil hole system 12 includes two oil inlets and three oil outlets. Each oil inlet of the high-pressure oil hole system 12 is connected to a corresponding high-pressure oil hole 21, and each oil outlet of the high-pressure oil hole system 12 is connected to the inner wall surface 10. Other components and connection methods are the same as Specific Embodiment 6.

[0048] In this embodiment, the high-pressure oil hole system 12 is directly connected to the oil film in the bearing to provide high-pressure lubricating oil. The diameter setting of the high-pressure oil hole system should not be too large to lose the throttling effect, nor should it be too small to cause the throttling effect to be too strong, resulting in a small flow rate and difficulty in flow regulation. The diameter setting must meet the following conditions: 1. The diameter of the high-pressure oil hole system is much larger than the oil film thickness; 2. The bearing diameter is much larger than the diameter of the high-pressure oil hole system. At the same time, in the scheme provided in this embodiment, of the two high-pressure oil holes 21 in the same group, only the high-pressure oil hole 21 connected to the arc-shaped oil cavity is used for oil supply, while the other high-pressure oil hole 21 is in a sealed state. When the bearing body 3 is separated from the outer shell 1 and the intermediate shell 2 and used alone, the two high-pressure oil holes 21 are in a connected state for connecting with the external high-pressure oil supply end. At this time, the bearing body 3 is used as a traditional passive sliding bearing.

[0049] Specific implementation method eight: combination Figures 1 to 18 This embodiment is described. The difference between this embodiment and the seventh embodiment is that the number of the inner oil grooves 9 is an even number. The other components and connection methods are the same as those of the seventh embodiment.

[0050] In this embodiment, since the number of inner oil grooves 9 is the same as the number of inner wall surfaces 10, in order to ensure that the oil output of the high-pressure oil hole system 12 connected to the inner wall surface 10 can be relatively stable, the number of inner oil grooves 9 and the number of inner wall surfaces 10 must be set to an even number.

[0051] Specific implementation method nine: combination Figures 1 to 18 This embodiment is described. The difference between this embodiment and the eighth embodiment is that a plurality of micro-textures 27 are evenly distributed on the inner wall surface 10. The other components and connection methods are the same as those of the eighth embodiment.

[0052] In this embodiment, a Tesla valve-type micro-texture 27 is arranged on the surface of the inner bearing surface 10. The arrangement of the micro-texture 27 includes but is not limited to a rectangular arrangement. The setting of the micro-texture 27 can generate more micro-convergent wedges and expansion wedges on the inner bearing surface 10, thereby enhancing the dynamic pressure effect of the bearing and improving the bearing's load-bearing capacity and dynamic performance.

[0053] Specific implementation method ten: Combination Figures 1 to 18 This embodiment is described. This embodiment differs from the ninth embodiment in that a low-pressure oil hole 22 is machined on the outer circumferential surface of the outer housing 1, a low-pressure oil hole 23 is machined on the outer circumferential surface of the intermediate housing 2, and a low-pressure oil supply annular groove 24 is machined on the outer circumferential surface of the bearing body 3. One end of the low-pressure oil hole 22 is connected to the oil outlet pipe of the high-pressure oil supply mechanism, and the other end of the low-pressure oil hole 22 is correspondingly connected to one end of the low-pressure oil hole 23 of the inner housing. The other end of the low-pressure oil hole 23 is connected to the low-pressure oil supply annular groove 24. The bottom of the low-pressure oil supply annular groove 24 is machined with multiple low-pressure oil holes 8 equidistantly spaced along the circumference. Each low-pressure oil hole 8 is correspondingly located between an inner oil groove 9 and the low-pressure oil supply annular groove 24. One end of each low-pressure oil hole 8 is connected to the low-pressure oil supply annular groove 24, and the other end of each low-pressure oil hole 8 is connected to the corresponding inner oil groove 9. Other components and connection methods are the same as those of the ninth embodiment.

[0054] In this embodiment, a low-pressure oil passage is formed by the outer shell low-pressure oil hole 22, the inner shell low-pressure oil hole 23, the low-pressure oil supply ring groove 24 and multiple low-pressure oil holes 8 to maintain the dynamic pressure effect of the oil film, ensuring that there is always an oil film in the bearing gap.

[0055] The present invention has been disclosed as above with reference to preferred embodiments, but this is not intended to limit the present invention. Any technician familiar with the present invention can make slight changes or modifications to equivalent embodiments using the above-disclosed structures and technical contents without departing from the scope of the technical solution of the present invention. However, any simple modifications, equivalent changes, and modifications made to the above embodiments based on the technical essence of the present invention without departing from the content of the technical solution of the present invention are still within the scope of the technical solution of the present invention.

[0056] How it works

[0057] The specific working process of the active control intelligent dynamic and static pressure hybrid sliding bearing with integrated sensing and execution provided by the present application is as follows: when active control is not performed, the controller 14 is not turned on. At this time, the X-direction servo valve 4 and the Y-direction servo valve 6 are both in the closed state. However, due to the leakage characteristics of the X-direction servo valve 4 and the Y-direction servo valve 6, some lubricating oil will flow into the bearing body 3 through the passage formed by the servo valve oil supply hole, the arc-shaped oil cavity, the adapter oil supply hole 20, the bearing body high-pressure oil supply hole group and the multiple high-pressure oil hole system 12. Low-pressure oil is supplied in the bearing body 3. At this time, the bearing works as a round-pad sliding bearing, relying only on the dynamic pressure effect of the bearing to provide bearing capacity;

[0058] In addition, when the sine signal or step signal is output to the controller 14 through the signal generator or the upper computer, the valve core of the X-direction servo valve 4 and the Y-direction servo valve 6 can be made to move periodically or step by step, which will cause the oil flow supplied to the bearing body 3 to change, and then generate a liquid sine periodic excitation force or impact excitation, so as to excite the rotor part, at this time, the bearing can be used as a hydraulic exciter;

[0059] When active control is performed, the controller 14 is turned on, the rotor displacement signals collected by the X-direction sensor 11 and the Y-direction sensor 13 are transmitted to the controller 14, the control signals of the X-direction servo valve 4 and the Y-direction servo valve 6 are calculated through a control algorithm, the X-direction servo valve 4 and the Y-direction servo valve 6 further control the flow of the injected oil, and a controllable active oil film force is generated to compensate for the change of the working condition and improve the stability and reliability of the bearing;

[0060] The integrated sensing and executing active control intelligent dynamic and static pressure hybrid sliding bearing has good stability and reliability as a passive device, has the function of a hydraulic exciter, can further compensate for the change of the working condition when the active control is turned on, further suppresses the vibration of the rotor, and has higher stability and carrying capacity.

Claims

1. An actively controlled intelligent dynamic and static hybrid sliding bearing with integrated sensing and execution, characterized by: The dynamic and static pressure hybrid sliding bearing comprises an outer shell (1), an intermediate shell (2), a bearing body (3), an X-direction servo valve (4), a Y-direction servo valve (6) and a servo valve control system, wherein the outer shell (1) is sleeved on the intermediate shell (2), the intermediate shell (2) is sleeved on the bearing body (3), and the outer shell (1), the intermediate shell (2) and the bearing body (3) are coaxially arranged, the X-direction servo valve (4) and the Y-direction servo valve (6) are both mounted on the outer circumferential surface of the outer shell (1), and the X-direction servo valve (4) is arranged relative to the Y-direction servo valve ( 6) It is set at 90 degrees offset, the signal input end of the servo valve control system is installed on the outer shell (1), and the signal output end of the servo valve control system is connected to the control end of the X-direction servo valve (4) and the control end of the Y-direction servo valve (6) through a wire. The high-pressure oil passes through the X-direction servo valve (4) and the Y-direction servo valve (6) and then passes through the outer shell (1) and the intermediate shell (2) in turn and finally enters between the bearing body (3) and the shaft system to form an active oil film. The servo valve control system is used to control the working state of the X-direction servo valve (4) and the Y-direction servo valve (6); Two oil supply hole groups are provided on the outer circumferential surface of the outer shell (1), one oil supply hole group is corresponding to the X-direction servo valve (4), and the other oil supply hole group is corresponding to the Y-direction servo valve (6). Each oil supply hole group includes an oil supply hole (16) at the A end of the servo valve and an oil supply hole (17) at the B end of the servo valve, and each group of oil supply holes (16) at the A end of the servo valve and the oil supply hole (17) at the B end of the servo valve is connected to the oil outlet end of the corresponding X-direction servo valve (4) or the oil outlet end of the Y-direction servo valve (6). Two outer shell oil groove groups are machined on the inner circumferential surface of the outer shell (1), each outer shell oil groove group is corresponding to an oil supply hole group, and each outer shell oil groove group includes two outer shell oil grooves (18), one outer shell oil groove (18) is connected to the oil supply hole (16) at the A end of the servo valve in the corresponding oil supply hole group, and the other outer shell oil groove (18) is connected to the oil supply hole (17) at the B end of the servo valve in the corresponding oil supply hole group. An X-direction servo valve connection seat is provided on the outer shell (1) at a position corresponding to the X-direction servo valve (4). The X-direction servo valve (4) is mounted on the X-direction servo valve connection seat. An X-direction high-pressure oil supply hole (5) is provided on the X-direction servo valve connection seat. The oil inlet end of the X-direction servo valve (4) is connected to the No. 1 oil outlet pipe of the high-pressure oil supply mechanism through the X-direction high-pressure oil supply hole (5). The oil outlet end of the X-direction servo valve (4) is connected to the corresponding servo valve A end oil supply hole (16) and the servo valve B end oil supply hole (17). A Y-direction servo valve connection seat is provided on the outer shell (1) at a position corresponding to the Y-direction servo valve (6), the Y-direction servo valve (6) is mounted on the Y-direction servo valve connection seat, a Y-direction high-pressure oil supply hole (7) is provided on the Y-direction servo valve connection seat, the oil inlet end of the Y-direction servo valve (6) is connected to the No. 2 oil outlet pipe of the high-pressure oil supply mechanism through the Y-direction high-pressure oil supply hole (7), and the oil outlet end of the Y-direction servo valve (6) is connected to the corresponding servo valve A end oil supply hole (16) and the servo valve B end oil supply hole (17); Two inner shell oil groove groups are machined on the outer circumferential surface of the intermediate shell (2), each inner shell oil groove group is arranged correspondingly to an outer shell oil groove group, each inner shell oil groove group includes two inner shell oil grooves (19), each inner shell oil groove (19) is arranged correspondingly to an outer shell oil groove (18), each inner shell oil groove (19) and the corresponding outer shell oil groove (18) are assembled into a complete arc-shaped oil cavity, and a transfer oil supply hole (20) is machined on the bottom of the inner shell oil groove (19), and each transfer oil supply hole (20) and the servo valve A end oil supply hole (16) or the servo valve B end oil supply hole (17) located in the same arc-shaped oil cavity are respectively arranged at both ends of the arc-shaped oil cavity.

2. The active control intelligent dynamic and static pressure hybrid sliding bearing with integrated sensing and execution according to claim 1 is characterized by: The servo valve control system comprises an X-direction sensor (11), a Y-direction sensor (13), a controller (14) and an electro-hydraulic servo driver (15). The X-direction sensor (11) and the Y-direction sensor (13) are both fixed on one end face of the outer shell (1) through a sensor mounting frame, and the X-direction sensor (11) is arranged corresponding to the X-direction servo valve (4), and the Y-direction sensor (13) is arranged corresponding to the Y-direction servo valve (6). The controller (14) and the electro-hydraulic servo driver (15) are both arranged outside the outer shell (1). The signal output end of the X-direction sensor (11) and the signal output end of the Y-direction sensor (13) are both connected to the signal input end of the controller (14) through a wire, the signal output end of the controller (14) is connected to the signal input end of the electro-hydraulic servo driver (15) through a wire, and the signal output end of the electro-hydraulic servo driver (15) is respectively connected to the control end of the X-direction servo valve (4) and the control end of the Y-direction servo valve (6) through a wire.

3. The active control intelligent dynamic and static pressure hybrid sliding bearing with integrated sensing and execution according to claim 2, characterized in that: Two oil return ring grooves (25) are symmetrically processed on the inner ring surface of the bearing body (3) along the center line of the thickness direction of the bearing body (3), and a plurality of inner oil grooves (9) are equidistantly processed along the inner circumference of the bearing body (3) between the two oil return ring grooves (25), and both ends of each inner oil groove (9) are respectively connected to an oil return ring groove (25), and an inner wall surface (10) is formed between two adjacent inner oil grooves (9). A plurality of bearing body high-pressure oil supply hole groups are equidistantly processed along the circumferential direction on the outer cylindrical surface of the bearing body (3), and each bearing body high-pressure oil supply hole group is correspondingly arranged to an inner wall surface (10). A plurality of high-pressure oil hole systems (12) are equidistantly processed inside the bearing body (3) along the circumferential direction, and each high-pressure oil hole system (12) is located between a bearing body high-pressure oil supply hole group and an inner wall surface (10), one end of each high-pressure oil hole system (12) is connected to the bearing body high-pressure oil supply hole group, and the other end of each high-pressure oil hole system (12) is connected to the inner wall surface (10).

4. The active control intelligent dynamic and static pressure hybrid sliding bearing with integrated sensing and execution according to claim 3 is characterized by: The bearing body high-pressure oil supply hole group includes two high-pressure oil holes (21), and the two high-pressure oil holes (21) in the same group are symmetrically arranged along the center line of the width direction of the bearing body (3), and one high-pressure oil hole (21) in each bearing body high-pressure oil supply hole group is arranged corresponding to the corresponding arc-shaped oil cavity, and the high-pressure oil hole system (12) includes two oil inlet ends and three oil outlet ends, each oil inlet end of the high-pressure oil hole system (12) is connected to a high-pressure oil hole (21), and each oil outlet end of the high-pressure oil hole system (12) is connected to the inner wall surface (10).

5. The active control intelligent dynamic and static pressure hybrid sliding bearing with integrated sensing and execution according to claim 3 is characterized by: The number of the inner oil grooves (9) is an even number.

6. The active control intelligent dynamic and static pressure hybrid sliding bearing with integrated sensing and execution according to claim 3, characterized in that: The inner tile surface (10) is evenly processed with a plurality of micro-textures (27).

7. The active control intelligent dynamic and static hybrid sliding bearing with integrated sensing and execution according to claim 3, characterized in that: The outer cylindrical surface of the outer shell (1) is processed with an outer shell low-pressure oil hole (22), the outer cylindrical surface of the intermediate shell (2) is processed with an inner shell low-pressure oil hole (23), and the outer cylindrical surface of the bearing body (3) is processed with a low-pressure oil supply ring groove (24). One end of the outer shell low-pressure oil hole (22) is connected to the oil outlet pipe of the high-pressure oil supply mechanism, and the other end of the outer shell low-pressure oil hole (22) is correspondingly connected to one end of the inner shell low-pressure oil hole (23). The inner shell low-pressure oil hole (2 The other end of the low-pressure oil supply ring groove (3) is connected to the low-pressure oil supply ring groove (24), and the bottom of the low-pressure oil supply ring groove (24) is processed with a plurality of low-pressure oil holes (8) at equal intervals along the circumferential direction. Each low-pressure oil hole (8) is correspondingly arranged between an inner oil groove (9) and the low-pressure oil supply ring groove (24), and one end of each low-pressure oil hole (8) is connected to the low-pressure oil supply ring groove (24), and the other end of each low-pressure oil hole (8) is connected to the corresponding inner oil groove (9).

Images