CN110686038B - Piezoelectric self-balancing elastic support dry friction damper of rotary machine rotor supporting structure - Google Patents
Piezoelectric self-balancing elastic support dry friction damper of rotary machine rotor supporting structure Download PDFInfo
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- CN110686038B CN110686038B CN201911015747.3A CN201911015747A CN110686038B CN 110686038 B CN110686038 B CN 110686038B CN 201911015747 A CN201911015747 A CN 201911015747A CN 110686038 B CN110686038 B CN 110686038B
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/005—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion using electro- or magnetostrictive actuation means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/1201—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon for damping of axial or radial, i.e. non-torsional vibrations
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/1207—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by the supporting arrangement of the damper unit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/129—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-damping means
- F16F15/1292—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-damping means characterised by arrangements for axially clamping or positioning or otherwise influencing the frictional plates
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2222/00—Special physical effects, e.g. nature of damping effects
- F16F2222/04—Friction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2232/00—Nature of movement
- F16F2232/02—Rotary
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Abstract
The invention discloses a piezoelectric self-balancing elastic support dry friction damper of a rotary mechanical rotor supporting structure, which comprises an elastic support, a dynamic friction plate support, a static friction plate, a force sensor, a static friction plate support, a fixed plate and an axial split belleville spring. The dynamic friction plate is arranged on the elastic supporting dynamic friction plate bracket to form the dynamic friction assembly. The static friction plate and the force sensor are fixed on the static friction plate bracket to form a static friction assembly. And a friction pair is formed between the dynamic friction assembly and the static friction assembly. An axial split belleville spring with a piezoelectric actuator is arranged between the static friction plate bracket and the fixed plate. The positive pressure on the friction pair is changed through the piezoelectric actuator, so that the friction force is controlled, and active control on vibration and stability of the rotary mechanical rotor system is realized. The friction force on the dry friction damper can be precisely controlled in real time through the piezoelectric actuator, so that the dry friction damper has a wide application prospect in the vibration active control of a rotary mechanical rotor system.
Description
Technical Field
The invention relates to the field of rotary machinery, in particular to a piezoelectric self-balancing elastic supporting dry friction damper of a rotary machinery rotor supporting structure.
Background
With the advent of industry 4.0, the rotors of most rotating machines in modern industrial technology have been evolving towards flexible structures. The operating speed of the flexible rotor is generally above a critical speed of the first or several orders. The traditional elastic support is widely applied to the supercritical vibration suppression of the flexible rotor due to the characteristics of simple structure, easiness in implementation and the like. However, the typical elastic support, particularly the elastic support using rolling bearings, can provide very little damping for the rotor system and cannot meet the requirements of the rotor system for damping. Therefore, it is desirable to add additional dampers to the spring support to effectively alleviate the problems faced by the purely resilient support. Extrusion oil film dampers, metal rubber dampers and the like are main methods for increasing external damping, but the methods have high requirements on the accuracy and the reliability of process manufacturing and structural design, otherwise rotor vibration cannot be restrained to the greatest extent in complex actual working conditions, complex nonlinear response can be caused by severe nonlinear characteristics, and finally the elastic support vibration restraining effect is invalid.
In the device structure mentioned in the patent "a method and device for suppressing vibration of a rotor system with elastic support" (ZL 200410073346.0), complex nonlinear characteristics of the system occur due to a large friction force existing when the rotor is stationary. The damping mechanism in the patent belongs to passive control instead of active control, and the friction force cannot be adjusted in real time according to the motion state of the rotor. In the device proposed by the patent 'an elastic supporting dry friction damper electric control device' (ZL 200710017593.2), although the friction force can be adjusted, the friction force component generated by one side is not large enough, the vibration suppression effect of the damper is limited, and a large axial pressure is applied to an elastic support, so that the elastic support is unstable; in particular, the friction force on the friction pair is not only related to the positive pressure, but also to the friction coefficient on the friction pair. The friction coefficient is affected by the working temperature and working condition of the friction pair, so that the friction force cannot be accurately controlled by controlling the positive pressure on the friction pair.
Disclosure of Invention
In order to overcome the defects of complex structure, small adjustment range of dry friction force, difficult accurate control of dry friction force and the like of the dry friction damper in the prior art, the invention provides a piezoelectric self-balancing elastic supporting dry friction damper of a rotary mechanical rotor supporting structure.
The technical scheme adopted by the invention is that a piezoelectric self-balancing dry friction damper with controllable dynamic characteristics is arranged on an elastic support of a rotor of a rotary machine, the friction force on a friction pair in the friction damper is changed through a piezoelectric actuator, and controllable external damping is introduced for a rotor system, so that active control on vibration and stability of the rotor system is realized.
The aim of the invention is realized by the following technical scheme: a piezoelectric self-balancing elastic support dry friction damper of a rotary machine rotor support structure comprises a bearing seat, a rotating shaft, a bearing, an elastic support, a left dynamic friction plate, a right dynamic friction plate, a dynamic friction plate support, a left static friction plate, a right static friction plate, a left force sensor, a right static friction plate support, a left axial disc split spring, a right axial disc split spring, an axial pre-pressing spring, a fixing ball and a damper shell. The left and right movable friction plates and the movable friction plate support form a movable friction assembly, and the left and right static friction plates, the left and right force sensors and the left and right static friction plate supports form left and right static friction assemblies.
The left and right movable friction plates are respectively fixed on two sides of the movable friction plate support, the movable friction plate support can be a part of an elastic support, and also can be a part fixed on one end of the elastic support, the inner circular surface of the elastic support is connected with the rotating shaft through a bearing, and the other end of the elastic support is fixed on the bearing seat through the elastic support.
The left and right static friction components are of symmetrical structures, the static friction plates are fixed on the force sensor, the force sensor is fixed on the inner side of the static friction plate bracket, the static friction plates are higher than the static friction plate bracket, and a certain gap is reserved between the static friction plates and the force sensor and the static friction plate bracket; the static friction plate support is matched with an outer positioning ball in the damper shell to complete radial and circumferential positioning.
The axial pre-pressing spring is arranged between the two static friction plate brackets and at the outer side of the dynamic friction plate bracket; the two ends of the axial pre-pressing spring are fixed by the positioning surfaces on the left and right static friction plate brackets or the outer surface of the axial pre-pressing spring and the positioning ball fittings in the damper shell are used for completing radial and circumferential positioning. The axial pre-pressing spring is in sliding connection with the positioning surfaces on the left static friction plate bracket and the right static friction plate bracket.
The left and right axial disc split springs are respectively arranged between the left and right static friction plate brackets and the left and right fixing plates, one end of each split spring is fixed on the left and right fixing plates, and the other end of each split spring is in sliding connection with the left and right static friction plate brackets. Each valve of the axial disc split spring is provided with a piezoelectric actuator, the positive pressure on a friction pair between the dynamic friction plate and the static friction plate is changed by controlling the voltage on the piezoelectric actuator, and then the dry friction force is controlled, so that the active control on the vibration and the stability of the rotary mechanical rotor system is realized. The piezoelectric actuator can be arranged on one side of each valve or on two sides.
The left and right fixing plates are internally fixed with axial disc split springs, the outside is connected with the damper shell through bolts, elastic gaskets are arranged between the outside and the damper shell in a cushioning mode, and the positions of the left and right fixing plates are adjusted through adjusting pre-pressure on the bolts.
The left and right dynamic friction plates, the left and right static friction components, the left and right axial disc split springs and the axial pre-compression springs are of symmetrical structures, the left and right static friction components and the axial pre-compression springs are all circumferentially and radially limited through positioning balls with small friction damping, the moving parts can flexibly move in the axial direction, the dry friction damper has a self-balancing function, the positive pressures formed on the left and right friction pairs are equal in size and opposite in direction, and the whole dry friction damper does not generate axial force on the elastic support.
The main working mode of the invention is as follows: when vibration and stability of the rotor system are required to be actively controlled by changing damping of the elastic support, firstly, voltage required to be applied to piezoelectric actuators on axial disc split springs on the left side and the right side is determined according to the required dry friction force, under the action of control voltage, the axial disc split springs on the left side and the right side generate axial acting force on a left static friction plate bracket, a left static friction assembly and a right static friction assembly are close to a dynamic friction assembly, positive pressure is generated on two friction pairs, and then dry friction force is formed, so that vibration and stability of the rotary mechanical rotor system are controlled. The dry friction force on the friction pair can be controlled in real time through the voltage on the piezoelectric actuator, so that the vibration and the stability of the rotor system can be actively controlled.
The piezoelectric self-balancing elastic support dry friction damper has two working modes, one is that in the state that the piezoelectric actuator does not work, the left and right fixing plates are adjusted to enable the axial disc split springs and the axial pre-compression springs at the left and right sides to be in a pressed state, but no obvious positive pressure is generated on the friction pair, and then the piezoelectric actuator on the axial disc split springs at the left and right sides is used for applying positive pressure to the friction pair to generate the required dry friction force. The other is that the axial disc split springs and the axial pre-compression springs at the left side and the right side are both in a pressed state by adjusting the positions of the left fixing plate and the right fixing plate under the non-working state of the piezoelectric actuator, a certain positive pressure is generated on the friction pair, and then the magnitude of the positive pressure on the friction pair is changed through the piezoelectric actuators on the axial disc split springs at the left side and the right side, so that the dry friction force is controlled.
Compared with the prior art, the invention has the beneficial effects that 1) the moving parts adopt rolling bearings, the structure is simple, the axial movement is flexible, the response speed is high, and the requirements of active control of vibration and stability of a rotor system of a high-speed rotating machine can be met; 2) The voltage on the piezoelectric actuator is regulated on line, so that the friction force is directly and accurately controlled, the influence of friction coefficient change caused by temperature, working state and the like on a friction surface on the friction force control precision in the friction force control process by controlling the positive pressure on the friction pair is avoided, and the control precision is improved; 3) The control range of the damping force of the dry friction damper is large, and the axial size of the structure is small; 4) Has self-balancing function and does not generate additional axial force on the elastic support.
Drawings
FIG. 1 is a schematic diagram of a piezoelectric self-balancing elastic support dry friction damper of a rotary machine rotor support structure with axial preload springs employing belleville springs;
FIG. 2 is a cross-sectional view of a piezoelectric self-balancing spring-supported dry friction damper of a rotary machine rotor support structure with a belleville spring for an axial preload spring;
FIG. 3 is a schematic diagram of the distribution of the axial belleville spring structure and the piezoelectric actuator;
in the figure: 1. a rotating shaft; 2. an elastic support; 3. an elastic support bracket; 4. a bearing seat; 5. a bearing; 6. a dynamic friction plate bracket; 7A, right dynamic friction plate; 7B, a left dynamic friction plate; 8A, a right static friction plate; 8B, a left static friction plate; 9A, right force sensor; 9B, a left force sensor; 10A, a right axial disc split spring; 10B, a left axial disc split spring; 11A, a right static friction plate bracket; 11B, a left static friction plate bracket; 12. an axial pre-pressing spring; 13A, a right fixing plate; 13B, a left fixing plate; 14. a positioning ball; 15. a damper housing.
Detailed Description
The following describes the embodiments of the present invention in further detail with reference to the drawings.
As shown in fig. 1, the piezoelectric self-balancing elastic support dry friction damper of the rotor support structure of the rotary machine provided by the invention comprises a rotating shaft 1; an elastic support 2; an elastic support bracket 3; a bearing seat 4; a bearing 5; a dynamic friction plate bracket 6; a right dynamic friction plate 7A; a left movable friction plate 7B; a right static friction plate 8A; a left static friction plate 8B; a right force sensor 9A; a left force sensor 9B; the right axial precompression disc split spring A10A; a left axial pre-pressing disc split spring 10B; a right static friction plate bracket 11A; a left static friction plate bracket 11B; an axial pre-compression spring 12; a right fixing plate 13A; a left fixing plate 13B; a right detent ball 14; a damper housing 15. Wherein:
the dynamic friction plate bracket 6, the right dynamic friction plate 7A and the left dynamic friction plate 7B form a dynamic friction assembly of the dry friction damper; the right static friction plate 8A, the right force sensor 9A, the right static friction plate bracket 11A and the right axial disc split spring 10A form a right static friction assembly of the dry friction damper; the left static friction plate 8B, the left force sensor 9B, the left static friction plate bracket 11B and the left axial precompressed disc split spring 11B form a left static friction component of the dry friction damper.
The right dynamic friction plate 7A, the left dynamic friction plate 7B, the right static friction plate 8A and the left static friction plate 8B are all annular, and the outer diameter of the dynamic friction plate is slightly smaller than that of the static friction plate; the inner diameter of the dynamic friction plate is slightly larger than that of the static friction plate.
The dynamic friction plate bracket 6 is fixed at one end of the elastic support 2, the right dynamic friction plate 7A and the left dynamic friction plate 7B are respectively fixed at two sides of the dynamic friction plate bracket 6, the left dynamic friction plate 7A and the right dynamic friction plate 7B are higher than the dynamic friction plate bracket 6, the inner surface of one end of the elastic support 2 is connected with the rotating shaft 1 through the bearing 5, and the whole elastic support structure is fixed on the bearing seat 4 through the elastic support bracket 3 at the left side.
The right static friction plate 8A and the left static friction plate 8B are fixed on the right force sensor 9A and the left force sensor 9B, then the right force sensor 9A and the left force sensor 9B are respectively fixed on the right static friction plate bracket 11A and the left static friction plate bracket 11B, and certain gaps are reserved among the right static friction plate bracket 11A and the left static friction plate bracket 11B, respectively, by the right static friction plate 8A, the left static friction plate 8B, the right force sensor 9A and the left force sensor 9B. The right static friction plate 8A and the left static friction plate 8B are higher than the static friction plate bracket. The outer surfaces of the left and right static friction plate brackets 11A and 11B are in clearance-free or micro-clearance fit with the positioning balls 14 in the damper housing 15 to complete radial and circumferential positioning, but can flexibly move in the axial direction.
The right dynamic friction plate 7A, the left dynamic friction plate 7B, the right static friction plate 8A and the left static friction plate 8B can be equal-thickness circular rings or fan-shaped or ring-shaped structures with matrix structures, and the materials of the dynamic friction plates can be steel, copper, powder metallurgy, carbon-carbon composite materials and other combinations.
The axial pre-pressing springs 12 are of symmetrical structures and are positioned between the left static friction plate bracket 11A and the right static friction plate bracket 11B; the axial pre-compression spring 12 can be positioned by the left and right static friction plate brackets 11A and 11B, and radial and circumferential positioning can be finished by adopting gapless or micro-clearance fit between the outer surface of the axial pre-compression spring 12 and the positioning ball 14 in the damper housing 15, but the axial pre-compression spring can flexibly move in the axial direction. The axial pre-compression spring 12 is slidably connected with the left and right static friction plate brackets 11A and 11B.
Each of the left and right axial disc split springs 10A and 10B is provided with a piezoelectric actuator, the piezoelectric actuators can be arranged on one side of each of the left and right axial disc split springs or on both sides of each of the left and right axial disc split springs, the axial force of the axial disc split springs 10A and 10B on the static friction assembly can be controlled by controlling the voltage on the piezoelectric actuators, the axial positive pressure on the two friction pairs is changed, the magnitude of the friction force is controlled, and therefore necessary damping is added to a rotor system through elastic support, and active control on vibration and stability of the rotor system is achieved.
The inner parts of the left and right fixing plates 13A and 13B are fixedly provided with axial disc split springs 10A and 10B, the left and right fixing plates 13A and 13B are connected with the damper housing 15 through bolts, elastic gaskets are arranged between the left and right fixing plates 13A and 13B and the damper housing 15, and the states of the axial pre-compression springs 12 and the axial disc split springs 10A and 10B and the contact force between friction pairs are changed through the adjustment of the positions of the left and right fixing plates 13A and 13B.
As shown in fig. 2, in order to improve the positioning accuracy of the left and right static friction components in the circumferential direction and the radial direction and the flexibility of movement in the axial direction, a plurality of rolling pairs which are uniformly distributed in the circumferential direction and are composed of a plurality of positioning balls 14 are arranged between the left and right static friction plate brackets 11A and 11B and the dry friction damper housing 15, the number of the rolling pairs is at least not lower than 3, the rolling pairs are arranged in the roller paths of the positioning balls 14 of the dry friction damper housing 15, and the surfaces of the positioning balls are exposed out of the inner surfaces of the housing to a certain height, but the falling of the balls is ensured.
In order to improve the movement flexibility of the axial movement of the left and right static friction assemblies, the rollaway nest of the positioning ball 14 can be filled with a lubricating material corresponding to working conditions, the lubricating material at low temperature can be common lubricating ester, and the lubricating material at high temperature can be graphite, solid lubricating powder and the like.
In order to improve the control accuracy, axial force and shear force sensors 9A and 9B are provided between the left and right static friction plates 8A and 8B and the left and right static friction plate holders 11A and 11B, and positive pressure on friction pairs between the dynamic friction plates 7A and 7B and the static friction plates 8A and 8B and the resultant dry friction force are accurately measured. In order to reduce the influence of friction coefficient change caused by the working temperature and working condition of the friction pair on the friction force control precision and improve the control precision, a closed-loop control system related to the voltage on the piezoelectric actuator can be formed by taking the required friction force as a target, so that the friction force can be accurately controlled.
The left and right fixing plates 13A and 13B are connected with the damper housing 15 through bolts, and spring gaskets are filled between the left and right fixing plates 13A and 13B and the damper housing 15.
When vibration and stability of the rotor system are required to be controlled through external damping on the elastic support, firstly, the voltage of the piezoelectric actuator on the axial belleville spring is determined according to the required dry friction force, under the action of control voltage, the axial belleville spring generates axial force, the two static friction assemblies approach to the corresponding dynamic friction plates 7A and 7B, and axial positive pressure is generated on friction pairs between the dynamic friction plates 7A and 7B and the static friction plates 8A and 8B, so that dry friction force is generated, and necessary damping is provided for the rotor system. The dry friction force on the friction pair can be controlled in real time through the voltage on the piezoelectric actuator, so that the active control on the vibration and the stability of the rotor system can be realized.
When assembled:
firstly, the piezoelectric actuator is installed on each valve of the axial disc split spring according to the structural position requirement, and the outgoing line of the piezoelectric actuator is connected in parallel.
Then, the movable friction assembly is installed according to the structural position requirement, and for the structure of the movable friction plate bracket 6 integrated with the elastic support, first, the right movable friction plate 7A and the left movable friction plate 7B are respectively fixed on two sides of the movable friction plate bracket 6, the outer surfaces of the two movable friction plates are kept parallel, and after the movable friction plates 7A and 7B are installed, the movable friction plate bracket 6 is protruded. For the structure of the movable friction plate bracket 6 which is separated from the elastic support, the movable friction plate bracket 6 is fastened at one end of the elastic support, then the right movable friction plate 7A and the left movable friction plate 7B are respectively fixed at two sides of the movable friction plate bracket 6, the outer surfaces of the two movable friction plates are kept parallel, and after the movable friction plates 7A and 7B are installed, the movable friction plate bracket 6 is protruded.
Further, the left and right static friction plates 8A and 8B are fixed on the left and right force sensors 9A and 9B, respectively, according to the structural position requirements, and then the force sensors 9A and 9B are fixed on the static friction plate supports 11A and 11B, and after installation, the static friction plates 8A and 8B protrude out of the static friction plate supports 11A and 11B, so that a left and right static and dynamic friction assembly is formed.
Further, the positioning balls 14 and the lubricating material are mounted in the damper housing 15 according to the structural position requirement, and the end portions are simply fixed.
Further, left and right axial disc split springs 10B and 10A are installed in the left and right fixing plates 13B and 13A according to the structural position requirement, and the lead wires are fixed.
Further, the dry friction damper is assembled according to the structural position requirement, the left static friction assembly can be firstly arranged on the left side of the damper shell 15 according to the requirement, and the fixing plate 13B with the axial disc split spring 10B is arranged and fixed on the damper shell 15; then installing a dynamic friction assembly and an axial pre-compression spring 12; the right static friction assembly and right fixing plate 13A with right axial disc split spring 10A are then installed and fixed to damper housing 15.
Further, the assembled dry friction damper is adjusted, and the left and right axial pre-pressing disc split springs 10A and 10B and the axial pre-pressing spring 12 are brought into a compressed state by adjusting the pre-tightening force of the bolts between the left and right fixing plates 13A and 13B and the damper housing 15, and a zero pressure contact state or a required positive pressure contact state on the friction pair is realized.
Finally, the left end of the elastic support 2 is fixed to the elastic support bracket 3 by bolts, the elastic support 3 is fixed at the left end of the bearing seat 4 by screws, the inner surface of the right end of the elastic support 2 is connected with the rotating shaft 1 by a bearing 5, and the outer side of the inner ring of the bearing is fixed by nuts or other modes. The housing 15 of the whole dry friction damper is fixed on the bearing seat 4, and the assembly of the whole dry friction damper is completed.
When vibration and stability of the rotor system are required to be controlled through external damping on the elastic support, the voltage of the piezoelectric actuator on the axial disc split spring is determined according to the required dry friction force, so that positive pressure generated on friction pairs of the dynamic friction plates 7A and 7B and the static friction plates 8A and 8B is regulated, the control of the dry friction force is realized, and the necessary damping is provided for the rotor system. The dry friction force between the dynamic friction plate and the static friction plate can be controlled in real time through the control voltage on the piezoelectric actuator, so that the dynamic friction plate has the advantages of being quick in frequency response, wide in axial force change range and the like, and vibration and stability of a rotor system can be actively controlled.
The above-described embodiments are intended to illustrate the present invention, not to limit it, and any modifications and variations made thereto are within the spirit of the invention and the scope of the appended claims.
Claims (7)
1. The piezoelectric self-balancing elastic support dry friction damper of the rotary machine rotor support structure is characterized by comprising a bearing seat, a rotating shaft, a bearing, an elastic support, left and right movable friction plates, a movable friction plate support, left and right static friction plates, left and right force sensors, left and right static friction plate supports, left and right fixed plates, left and right axial disc split springs, axial pre-compression springs, positioning balls and damper shells; the left and right movable friction plates and the movable friction plate support form a movable friction assembly, and the left and right static friction plates, the left and right force sensors and the left and right static friction plate supports form left and right static friction assemblies respectively;
the left axial disc split spring is arranged between the left static friction plate bracket and the left fixed plate, one end of the left axial disc split spring is fixed on the left fixed plate, and the other end of the left axial disc split spring is connected with the left static friction plate bracket in a sliding manner; the right axial disc split spring is arranged between the right static friction plate bracket and the right fixed plate, one end of the right axial disc split spring is fixed on the right fixed plate, and the other end of the right axial disc split spring is connected with the right static friction plate bracket in a sliding manner; each of the petals of the axial disc split spring is provided with a piezoelectric actuator which is arranged on one side of each petal only, or on both sides of each petal.
2. The piezoelectric self-balancing elastic supporting dry friction damper of a rotary machine rotor supporting structure according to claim 1, wherein the left and right movable friction plates are respectively fixed on two sides of the movable friction plate bracket, the left and right movable friction plates protrude out of the movable friction plate bracket, and the inner circular surface of the elastic support is connected with the rotating shaft through a bearing.
3. The piezoelectric self-balancing elastic supporting dry friction damper of a rotary machine rotor supporting structure according to claim 1, wherein the left and right static friction components are of symmetrical structure, the static friction plates are fixed on the force sensor, the force sensor is fixed on the static friction plate bracket, and the static friction plates are higher than the static friction plate bracket; the left and right static friction plates, the outer rings of the left and right force sensors and the left and right static friction plate brackets have certain gaps, and the left and right static friction plate brackets are matched with positioning balls in the damper shell to complete radial and circumferential positioning.
4. The piezoelectric self-balancing elastic supporting dry friction damper of a rotary machine rotor supporting structure according to claim 1, wherein the left and right fixing plates are installed at the outer sides of the left and right static friction assemblies and fixed at both sides of the damper housing.
5. The piezoelectric self-balancing elastic supporting dry friction damper of a rotary machine rotor supporting structure according to claim 1, wherein the axial pre-compression spring is arranged between the left and right static friction plate brackets, and is positioned by positioning surfaces on the left and right static friction plate brackets, or the outer ring of the axial pre-compression spring is matched with positioning balls in the damper shell to complete radial and circumferential positioning; the axial pre-compression spring is connected with the positioning surfaces on the left and right static friction plate brackets in a sliding manner; the axial pre-pressing spring adopts a disc spring or an annular spring or metal rubber.
6. The piezoelectric self-balancing elastic supporting dry friction damper of a rotor supporting structure of a rotary machine according to claim 1, wherein the dynamic friction plate and the static friction plate are of equal-thickness circular rings or of sector or ring structures with matrix structures, and the materials of the dynamic friction plate and the static friction plate are a combination of steel, copper, powder metallurgy and carbon-carbon composite materials.
7. The piezoelectric self-balancing elastic supporting dry friction damper of the rotary machine rotor supporting structure according to claim 1, wherein the left and right dynamic friction plates, the left and right static friction components, the left and right axial disc split springs and the axial pre-compression springs are all symmetrical structures and have the characteristic of force self-balancing, and the positive pressure between the dynamic friction plates and the static friction plates is changed by controlling the voltage on the piezoelectric actuator, so that the dry friction force is accurately controlled, and active control on vibration and stability of a rotary machine rotor system is realized.
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