CN113758697A - Recognition method for dynamics coefficient of squeeze film damper - Google Patents

Recognition method for dynamics coefficient of squeeze film damper Download PDF

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CN113758697A
CN113758697A CN202111106390.7A CN202111106390A CN113758697A CN 113758697 A CN113758697 A CN 113758697A CN 202111106390 A CN202111106390 A CN 202111106390A CN 113758697 A CN113758697 A CN 113758697A
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supporting seat
elastic
damper
rotor
outer ring
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CN113758697B (en
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张广辉
黄延忠
陈亚龙
马会防
龚文杰
徐科繁
国阳
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Harbin Institute of Technology
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    • G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
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    • G01N3/00—Investigating strength properties of solid materials by application of mechanical stress
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Abstract

The invention relates to a method for identifying a dynamics coefficient of an extrusion oil film damper, which belongs to the field of rotor dynamics and aims to solve the problem that the existing experimental device is difficult to test the dynamics coefficient of the extrusion oil film damper in the rotating process of a rotor on site; according to the calibration of the relation between the strain and the force of cage bars in the elastic squirrel cage supporting seat and the damper outer ring supporting seat, the external transmission force of the dynamic excitation force of the rotor passing through the elastic squirrel cage supporting seat and the damper outer ring supporting seat is obtained, and the identification of the dynamics coefficient of the squeeze film damper is realized. The method can easily identify the dynamic coefficient of the squeeze film damper under different rotating speeds of the rotor.

Description

Recognition method for dynamics coefficient of squeeze film damper
Technical Field
The invention relates to the field of rotor dynamics, in particular to a method for identifying a dynamic coefficient of an extrusion oil film damper.
Background
The squeeze film damper is a mechanical structure with simple structure and friendly vibration reduction performance, is widely applied to aeroengines and gas turbines, effectively reduces the vibration of units and improves the operation reliability of equipment.
The dynamic coefficient is a key parameter for measuring the quality of the vibration reduction performance of the squeeze film damper, so that the measurement of the dynamic coefficient (particularly the damping coefficient) of the squeeze film damper is necessary, particularly, the damping coefficient at different rotating speeds is obtained when a rotor normally works, the vibration reduction performance of the damper is favorably quantized, and a reference is provided for the subsequent optimization design of the damper.
Disclosure of Invention
The invention aims to solve the problem that the dynamic coefficient of the squeeze film damper in the rotating process of a rotor is difficult to test on site by using the conventional experimental device, and further provides a method for identifying the dynamic coefficient of the squeeze film damper;
a method for identifying dynamics coefficients of an extruded oil film damper is characterized by comprising the following steps: the identification method is realized by the following steps:
the method comprises the following steps: determining elastic squirrel cage bearing seat force transfer coefficient K in squeeze film damperin；
Step two: determining transmission coefficient K of outer ring supporting seat of damper in squeeze film damperout；
Step three: utilizing the force transfer coefficient K of the elastic squirrel cage supporting seat obtained in the step oneinDetermining the excitation force F transmitted by the rotor to the elastic squirrel cage bearing seat when the obtained rotating speed N is N r/minin|N＝n；
Step four: utilizing the force transfer coefficient K of the damper outer ring supporting seat obtained in the step twooutDetermining the excitation force F transmitted by the rotor to the elastic squirrel cage bearing seat when the obtained rotating speed N is N r/minout|N＝n；
Step five: the exciting force F obtained in the third step and transmitted to the elastic squirrel cage supporting seat by the rotor when the obtained rotating speed N is N r/min is utilizedin|N＝nAnd the excitation force F obtained in the fourth step and transmitted to the elastic squirrel cage supporting seat by the rotor when the obtained rotating speed N is N r/minout|N＝nDetermining the equivalent stiffness K of an oil film in a squeeze film damper0And equivalent damping C0；
Further, the force transfer coefficient K of the elastic squirrel cage supporting seat in the squeeze film damper is determined in the step oneinThe method is realized by the following steps:
the method comprises the following steps: the elastic squirrel cage bearing seat is arranged on the fixing device, an elastic squirrel cage bearing seat bearing plate is arranged at the mounting seam allowance of an elastic squirrel cage bearing seat bearing plate on the elastic squirrel cage bearing seat in an interference fit manner, a bearing rod penetrates through a central through hole of the elastic squirrel cage bearing seat bearing plate, and the force arms of the bearing rods at the two ends of the elastic squirrel cage bearing seat bearing plate are ensured to be the same;
the first step is: a first resistance strain gauge measuring terminal is pasted at the 1/4 position of the uppermost cage bar in the elastic cage supporting seat and the distance between the uppermost cage bar and the fixed end of the cage bar is the cage bar length, and the first resistance strain gauge measuring terminal is connected into an industrial data acquisition system through a first resistance strain gauge wiring and is used for monitoring and recording the strain change of the cage bars in the loading and unloading process;
step one is three: loading and unloading heavy objects at two ends of the bearing rod, wherein the two ends of the bearing rod are subjected to three loading-unloading processes in total, and the weight of the heavy objects changed each time is recorded, so that the load change borne by the elastic squirrel cage supporting seat can be obtained;
step one is: fitting according to the loading and unloading process data in the first step and the third step to obtain a force transmission-strain fitting result twice:
Fspring loading＝K1ε1 (1)
FCartridge unloading＝K2ε2 (2)
In the formula:
Fspring loadingStatic load applied to the elastic squirrel cage supporting seat in the loading process;
Fcartridge unloadingStatic load on the elastic squirrel cage supporting seat in the unloading process;
K1the load-strain relation coefficient fitted in the loading process is tested for the static load of the elastic squirrel cage supporting seat;
K2the load-strain relation coefficient fitted in the unloading process is tested for the static load of the elastic squirrel cage supporting seat;
ε1applying a load F for the loading processSpring loading(ii) strain;
ε2applied to the load F for the unloading processCartridge unloading(ii) strain;
step one and five: according to K obtained in the step one or four1And K2Is a reaction of K1And K2Average determination of elastic mouse cage support seat force transfer coefficient K by calculationin：
Figure BDA0003272463200000021
Further, the damper outer ring in the squeeze film damper is determined in the second stepCoefficient of transmission K of supporting seatoutThe method is realized by the following steps:
step two, firstly: installing the damper outer ring supporting seat on a fixing device, installing a damper outer ring supporting seat bearing plate at the mounting seam allowance of a damper outer ring supporting seat bearing plate on the damper outer ring supporting seat in an interference fit manner, penetrating a bearing rod into a central through hole of the damper outer ring supporting seat bearing plate, and ensuring that the force arms of the bearing rods at two ends of the damper outer ring supporting seat bearing plate are the same;
step two: a second resistance strain gauge measuring terminal is pasted on the uppermost cage bar of the damper outer ring supporting seat and at a position 1/4 which is as long as the cage bar from the fixed end of the cage bar, and the second resistance strain gauge measuring terminal is connected into an industrial data acquisition system through a second resistance strain gauge connecting wire and is used for monitoring and recording the strain change of the cage bar in the loading and unloading process;
step two and step three: loading and unloading heavy objects at two ends of the load-bearing rod, wherein the two ends of the load-bearing rod are subjected to three loading-unloading processes in total, and the weight of the heavy object changed each time is recorded, so that the load change borne by the damper outer ring supporting seat can be obtained;
step two, four: fitting according to the data of the loading and unloading processes in the second step and the third step to obtain a force transmission-strain fitting result twice:
Fexternal loading＝K3ε3 (4)
FExternal unloading＝K4ε4 (5)
In the formula:
Fexternal loadingStatic load applied to the damper outer ring support seat in the loading process;
Fexternal unloadingStatic load on the damper outer ring supporting seat in the unloading process;
K3the load-strain relation coefficient fitted in the loading process is tested for the static load of the damper outer ring supporting seat;
K4the load-strain relation coefficient fitted in the unloading process is tested for the static load of the damper outer ring supporting seat;
ε3applying a load F for the loading processExternal loading(ii) strain;
ε4applied to the load F for the unloading processExternal unloading(ii) strain;
step two and step five: according to K obtained in the step one or four3And K4Is a reaction of K3And K4Average determination of elastic mouse cage support seat force transfer coefficient K by calculationout：
Figure BDA0003272463200000031
Furthermore, the force transfer coefficient K of the elastic squirrel cage supporting seat obtained in the step one is utilized in the step threeinDetermining the excitation force F transmitted by the rotor to the elastic squirrel cage bearing seat when the obtained rotating speed N is N r/minin|N＝nThe method is realized by the following steps:
step three, firstly: the elastic squirrel cage supporting seat is arranged on the fixing device, a bearing is embedded at a bearing installation seam allowance on the elastic squirrel cage supporting seat, the bearing is in interference fit with a rotor with a balance hole, and the rotor with the balance hole is rotationally connected with the elastic squirrel cage supporting seat through the bearing;
step three: adhering a 0-degree elastic squirrel cage supporting cage bar resistance strain gauge, a 90-degree elastic squirrel cage supporting cage bar resistance strain gauge, a 180-degree elastic squirrel cage supporting cage bar resistance strain gauge and a 270-degree elastic squirrel cage supporting cage bar resistance strain gauge to an elastic squirrel cage supporting seat cage bar along the circumferential direction, ensuring that the length of the adhering position from the cage bar fixing end is 1/4 of the cage bar length, and monitoring the strain change of the elastic squirrel cage supporting cage bar in the working process of a rotor;
step three: when the rotor with the balance hole works normally, the strain amplitude of the elastic squirrel cage supporting seat at different rotating speeds is obtained:
εin＝ε(N)； (7)
step three and four: by combining the force transfer coefficient of the elastic squirrel cage supporting seat measured by the experiment, the excitation force transmitted to the elastic squirrel cage supporting seat by the rotor at the rotating speed N of N r/min can be obtained:
Fin|N＝n＝Kin×εin(N＝n)； (8)
further, the force transmission coefficient K of the damper outer ring supporting seat obtained in the second step is utilized in the fourth stepoutDetermining the excitation force F transmitted by the rotor to the outer ring bearing seat of the damper when the obtained rotating speed N is N r/minout|N＝nThe method is realized by the following steps:
step four, firstly: installing an extrusion oil film damper on a fixing device, wherein the extrusion oil film damper comprises an elastic squirrel cage supporting seat, an extrusion oil film damper end sealing ring and a damper outer ring supporting seat, the extrusion oil film damper end sealing ring is arranged between the elastic squirrel cage supporting seat and the damper outer ring supporting seat, so that an extrusion oil film is formed between the elastic squirrel cage supporting seat and the damper outer ring supporting seat, a bearing is embedded at a bearing installation seam allowance on the elastic squirrel cage supporting seat in the extrusion oil film damper, the bearing is in interference fit with a rotor with a balance hole, and the rotor with the balance hole is rotatably connected with the elastic squirrel cage supporting seat through the bearing;
step four and step two: adhering a 0-degree damper outer ring support seat cage bar resistance strain gauge, a 90-degree damper outer ring support seat cage bar resistance strain gauge, a 180-degree damper outer ring support seat cage bar resistance strain gauge and a 270-degree damper outer ring support seat cage bar resistance strain gauge to a damper outer ring support seat cage bar along the circumferential direction, ensuring that the length of the adhering position from the cage bar fixing end is 1/4 of the cage bar length, and monitoring the strain change of the damper outer ring support cage bar in the working process of a rotor;
step four and step three: arranging an X-direction rotor vibration eddy current displacement sensor and a Y-direction rotor vibration eddy current displacement sensor at positions, close to the extrusion damper, of a rotor with balance holes, wherein the X-direction rotor vibration eddy current displacement sensor and the Y-direction rotor vibration eddy current displacement sensor are arranged at 90 degrees to each other and are used for monitoring radial vibration displacement of the rotor during working;
step four: when the rotor with the balance hole works normally, acquiring the strain amplitude of the damper outer ring supporting seat at different rotating speeds:
εout＝ε(N)； (9)
step four and five: by combining the force transfer coefficient of the damper outer ring supporting seat measured by the experiment, the excitation force transmitted to the damper outer ring supporting seat by the rotor at the rotating speed N of N r/min can be obtained:
Fout|N＝n＝Kout×εout(N＝n)； (10)
further, the equivalent rigidity K of the oil film in the squeeze film damper in the fifth step0And equivalent damping C0The method is realized by the following steps:
step five, first: when the rotating speed N is N r/min, calculating the vector sum of the force transmitted to the oil film by the elastic squirrel cage supporting seat and the damper outer ring supporting seat as the external force born by the oil film:
Figure BDA0003272463200000051
step five two: the test sensor monitors the vibration displacement of the rotor as x and y, the rotor stably runs when the rotating speed N is N r/min, the precession track of the rotor is a circle, and the radial displacement of the rotor is calculated:
Figure BDA0003272463200000052
step five and step three: analyzing the external force transmission path of the rotor, further obtaining the equivalent dynamic coefficient of the squeeze film damper, and obtaining the equivalent stiffness K when the inner ring of the squeeze film damper performs circular precession when the rotating speed N is N r/min0And equivalent damping C0The coefficient calculation formula is:
Figure BDA0003272463200000053
Figure BDA0003272463200000054
in the formula:
K0the equivalent stiffness of the oil film is N r/min when the rotating speed N is equal to the speed;
C0oil film equivalent damping is achieved when the rotating speed N is N r/min;
Figure BDA0003272463200000055
the oil film force is the oil film force when the rotating speed N is N r/min;
e is the eccentric moment of the rotor in the vortex mode of circular precession;
wherein Ω is the angular frequency of the rotor vortex motion under the vortex motion form of circular precession, and the unit HZ can be calculated by the following formula in the experimental process of the rotor with only unbalanced excitation:
Figure BDA0003272463200000056
compared with the prior art, the invention has the following beneficial effects:
1. the method for identifying the dynamics coefficient of the squeeze film damper provided by the invention is low in cost by relying on a simple experimental device, and is widely suitable for identifying the dynamics coefficient of various squeeze film dampers.
2. According to the method for identifying the dynamics coefficient of the squeeze film damper, the force of the dynamic excitation force of the rotor transmitted to the elastic squirrel cage supporting seat can be obtained, and support is provided for the fatigue life optimization design of the elastic squirrel cage supporting seat.
3. The method for identifying the dynamic coefficient of the squeeze film damper provided by the invention is simple in calculation and strong in engineering property, and can easily acquire the change of the external force transmission of the rotor along with the rotating speed, thereby achieving the purpose of identifying the dynamic coefficient of the damper.
4. The method for identifying the dynamics coefficient of the squeeze film damper can identify the dynamics coefficient of the squeeze film damper under different rotating speeds when a rotor normally works, has more accurate result, and can provide reference for the subsequent optimization design of the damper.
Drawings
FIG. 1 is a front cross-sectional view of a fixture used in the squeeze film damper dynamics coefficient identification method of the present invention;
FIG. 2 is a front cross-sectional view of the elastic squirrel cage support base of the present invention;
FIG. 3 is a cross-sectional view of cage bars in the support block of the elastic cage of FIG. 2 (sticking azimuth of the resistance strain gauge);
FIG. 4 is a front sectional view of the outer ring support base of the damper of the present invention;
FIG. 5 is a cross-sectional view of a cage bar in the bearing block of the outer ring of the damper of FIG. 4 (sticking azimuth of the resistance strain gauge);
FIG. 6 is a schematic diagram of the relationship coefficient test of the supporting force-strain of the elastic squirrel cage in the invention;
FIG. 7 is a schematic diagram of a force-strain relationship coefficient test of the outer ring bearing of the damper according to the present invention;
FIG. 8 is a front view of the rotor external force measurement device;
FIG. 9 is a schematic view of a force transfer path of the rotor;
FIG. 10 is a schematic diagram of the sticking position of a resistance strain gauge on a cage bar of an elastic squirrel cage supporting seat;
FIG. 11 is a schematic diagram of the sticking position of the resistance strain gauge on the supporting seat cage bar of the damper outer ring.
In the figure, 1, a bearing support, 2, a bearing support rib plate, 3, a rotor with a balance hole, 4, 5, an elastic squirrel cage supporting seat, 6, an end seal ring of an extrusion oil film damper, 7, 8, 9, 10, 110, 1290, 13180 and 14270 degree elastic squirrel cage supporting cage bar resistance strain gauges; 150-degree damper outer ring support seat cage bar resistance strain gauge, 1690-degree damper outer ring support seat cage bar resistance strain gauge, 17180-degree damper outer ring support seat cage bar resistance strain gauge, 18270-degree damper outer ring support seat cage bar resistance strain gauge, 19-elasticity squirrel cage support seat bearing disc, 20-bearing rod, 21-weight, 22-degree resistance strain gauge measuring terminal, 23-degree resistance strain gauge wiring, 24-degree damper outer ring support seat bearing disc, 25-degree resistance strain gauge measuring terminal, 26-degree resistance strain gauge wiring, 27X-direction rotor vibration eddy current displacement sensor and 28Y-direction rotor vibration eddy current displacement sensor.
Detailed Description
The first embodiment is as follows: the present embodiment is described with reference to fig. 1 to 11, and provides a method for identifying a kinetic coefficient of a squeeze film damper, characterized in that: the identification method is realized by the following steps:
the method comprises the following steps: determining elastic squirrel cage bearing seat force transfer coefficient K in squeeze film damperin；
Step two: determining transmission coefficient K of outer ring supporting seat of damper in squeeze film damperout；
Step three: utilizing the force transfer coefficient K of the elastic squirrel cage supporting seat obtained in the step oneinDetermining the excitation force F transmitted by the rotor to the elastic squirrel cage bearing seat when the obtained rotating speed N is N r/minin|N＝n；
Step four: utilizing the force transfer coefficient K of the damper outer ring supporting seat obtained in the step twooutDetermining the excitation force F transmitted by the rotor to the elastic squirrel cage bearing seat when the obtained rotating speed N is N r/minout|N＝n；
Step five: the exciting force F obtained in the third step and transmitted to the elastic squirrel cage supporting seat by the rotor when the obtained rotating speed N is N r/min is utilizedin|N＝nAnd the excitation force F obtained in the fourth step and transmitted to the elastic squirrel cage supporting seat by the rotor when the obtained rotating speed N is N r/minout|N＝nDetermining the equivalent stiffness K of an oil film in a squeeze film damper0And equivalent damping C0。
The second embodiment is as follows: the present embodiment is described with reference to fig. 1 to 9, and is further limited to the first step of the first embodiment, in which the elastic squirrel cage bearing seat force transfer coefficient K in the squeeze film damper is determinedinThe method is realized by the following steps:
the method comprises the following steps: the elastic squirrel cage bearing seat 5 is arranged on a fixing device, an elastic squirrel cage bearing seat bearing plate 19 is arranged at the position of an elastic squirrel cage bearing seat bearing plate mounting seam allowance 5b on the elastic squirrel cage bearing seat 5 in an interference fit manner, a bearing rod 20 penetrates through a central through hole of the elastic squirrel cage bearing seat bearing plate 19, and the force arms of the bearing rods 20 at two ends of the elastic squirrel cage bearing seat bearing plate 19 are ensured to be the same;
the first step is: a first resistance strain gauge measuring terminal 22 is pasted at the position 1/4 where the uppermost cage bar 9 in the elastic cage supporting seat is away from the fixed end of the cage bar by the length of the cage bar, and the first resistance strain gauge measuring terminal 22 is connected into an industrial data acquisition system through a first resistance strain gauge connecting wire 23 and is used for monitoring and recording the strain change of the cage bar in the loading and unloading processes;
step one is three: loading and unloading heavy objects at two ends of the bearing rod 20, wherein the two ends of the bearing rod are subjected to three loading-unloading processes in total, and the weight of the heavy objects changed each time is recorded, so that the load change borne by the elastic squirrel cage supporting seat 5 can be obtained;
step one is: fitting according to the loading and unloading process data in the first step and the third step to obtain a force transmission-strain fitting result twice:
Fspring loading＝K1ε1 (1)
FCartridge unloading＝K2ε2 (2)
In the formula:
Fspring loadingStatic load applied to the elastic squirrel cage supporting seat in the loading process;
Fcartridge unloadingStatic load on the elastic squirrel cage supporting seat in the unloading process;
K1the load-strain relation coefficient fitted in the loading process is tested for the static load of the elastic squirrel cage supporting seat;
K2the load-strain relation coefficient fitted in the unloading process is tested for the static load of the elastic squirrel cage supporting seat;
ε1applying a load F for the loading processSpring loading(ii) strain;
ε2applied to the load F for the unloading processCartridge unloading(ii) strain;
step one and five: according to K obtained in the step one or four1And K2Is a reaction of K1And K2Average determination of elastic mouse cage support seat force transfer coefficient K by calculationin：
Figure BDA0003272463200000081
Other components and connection modes are the same as those of the first embodiment.
The fixing device mainly comprises a bearing support 1 and a bearing support rib plate 2, wherein the bearing support 1 is used for fixing the elastic squirrel cage support, the bearing support rib plate 2 plays a role in increasing strength, three loading-unloading processes are totally implemented in the first step and the third step, the amount of heavy substances changed each time is recorded, further load changes borne by the elastic squirrel cage support can be obtained, and load-strain data are collected and recorded in a table 1:
TABLE 1 force transfer-strain variation of elastic squirrel cage supporting seat
Figure BDA0003272463200000082
The third concrete implementation mode: the present embodiment is described with reference to fig. 1 to 11, and the present embodiment further defines the second step described in the second embodiment, and in the present embodiment, the force transmission coefficient K of the damper outer ring bearing seat in the squeeze film damper is determined in the second stepoutThe method is realized by the following steps:
step two, firstly: installing a damper outer ring supporting seat 7 on a fixing device, installing a damper outer ring supporting seat bearing plate 24 at a damper outer ring supporting seat bearing plate installing seam allowance 7a on the damper outer ring supporting seat 7 in an interference fit mode, penetrating a bearing rod 20 into a central through hole of the damper outer ring supporting seat bearing plate 24, and ensuring that the force arms of the bearing rods 20 at two ends of the damper outer ring supporting seat bearing plate 24 are the same;
step two: a second resistance strain gauge measuring terminal 25 is pasted on the uppermost cage bar 10 of the damper outer ring supporting seat and at the position 1/4 which is away from the fixed end of the cage bar by the length of the cage bar, and the second resistance strain gauge measuring terminal 25 is connected into an industrial data acquisition system through a second resistance strain gauge connecting wire 26 and is used for monitoring and recording the strain change of the cage bar in the loading and unloading process;
step two and step three: loading and unloading heavy objects at two ends of the load-bearing rod 20, wherein the two ends of the load-bearing rod are subjected to three loading-unloading processes in total, and the weight of the heavy object changed each time is recorded, so that the load change borne by the damper outer ring supporting seat 7 can be obtained;
step two, four: fitting according to the data of the loading and unloading processes in the second step and the third step to obtain a force transmission-strain fitting result twice:
Fexternal loading＝K3ε3 (4)
FExternal unloading＝K4ε4 (5)
In the formula:
Fexternal loadingStatic load applied to the damper outer ring support seat in the loading process;
Fexternal unloadingStatic load on the damper outer ring supporting seat in the unloading process;
K3the load-strain relation coefficient fitted in the loading process is tested for the static load of the damper outer ring supporting seat;
K4the load-strain relation coefficient fitted in the unloading process is tested for the static load of the damper outer ring supporting seat;
ε3applying a load F for the loading processExternal loading(ii) strain;
ε4applied to the load F for the unloading processExternal unloading(ii) strain;
step two and step five: according to K obtained in the step one or four3And K4Is a reaction of K3And K4Average determination of elastic mouse cage support seat force transfer coefficient K by calculationout：
Figure BDA0003272463200000091
The other components and the connection mode are the same as those of the second embodiment.
The fixing device mainly comprises a bearing support 1 and a bearing support rib plate 2, wherein the bearing support 1 is used for fixing the damper outer ring support, the bearing support rib plate 2 plays a role in increasing strength, three loading-unloading processes are totally implemented in the step two and the step three, the amount of heavy substances changed each time is recorded, further load change borne by the damper outer ring support can be obtained, and load-strain data are collected and recorded in a table 1:
TABLE 2 damper outer ring bearing seat force transfer-strain variation
Figure BDA0003272463200000092
Figure BDA0003272463200000101
The fourth concrete implementation mode: the present embodiment will be described with reference to fig. 1 to 11, and the present embodiment is further limited to the third step of the third embodiment, in which the force transfer coefficient K of the elastic squirrel cage supporting seat obtained in the first step is utilized in the third stepinDetermining the excitation force F transmitted by the rotor to the elastic squirrel cage bearing seat when the obtained rotating speed N is N r/minin|N＝nThe method is realized by the following steps:
step three, firstly: the elastic squirrel cage supporting seat 5 is arranged on the fixing device, a bearing 4 is embedded at a bearing installation seam allowance 5a on the elastic squirrel cage supporting seat 5, the bearing 4 is in interference fit with a rotor 3 with a balance hole, and the rotor 3 with the balance hole is rotationally connected with the elastic squirrel cage supporting seat through the bearing 4;
step three: sticking a 0-degree elastic squirrel cage supporting cage bar resistance strain gauge 11, a 90-degree elastic squirrel cage supporting cage bar resistance strain gauge 12, a 180-degree elastic squirrel cage supporting cage bar resistance strain gauge 13 and a 270-degree elastic squirrel cage supporting cage bar resistance strain gauge 14 on an elastic squirrel cage supporting seat cage bar 9 along the circumferential direction, ensuring that the sticking position is 1/4 the length of the cage bar from the fixed end of the cage bar, and monitoring the strain change of the elastic squirrel cage supporting cage bar 9 in the working process of a rotor;
step three: when the rotor 3 with the balance hole works normally, the strain amplitude of the elastic squirrel cage supporting seat at different rotating speeds is obtained:
εin＝ε(N)； (7)
step three and four: by combining the force transfer coefficient of the elastic squirrel cage supporting seat measured by the experiment, the excitation force transmitted to the elastic squirrel cage supporting seat by the rotor at the rotating speed N of N r/min can be obtained:
Fin|N＝n＝Kin×εin(N＝n)。 (8)
other components and connection modes are the same as those of the third embodiment.
The fifth concrete implementation mode: the present embodiment will be described with reference to fig. 1 to 11, and the present embodiment is further limited to the fourth step of the fourth embodiment, in which the force transmission coefficient K of the damper outer ring bearing seat obtained in the second step is used in the fourth stepoutDetermining the excitation force F transmitted by the rotor to the outer ring bearing seat of the damper when the obtained rotating speed N is N r/minout|N＝nThe method is realized by the following steps:
step four, firstly: installing an extrusion oil film damper on a fixing device, wherein the extrusion oil film damper comprises an elastic squirrel cage supporting seat 5, an extrusion oil film damper end sealing ring 6 and a damper outer ring supporting seat 7, the extrusion oil film damper end sealing ring 6 is arranged between the elastic squirrel cage supporting seat 5 and the damper outer ring supporting seat 7, so that an extrusion oil film is formed between the elastic squirrel cage supporting seat 5 and the damper outer ring supporting seat 7, a bearing 4 is embedded at a bearing installation spigot 5a on the elastic squirrel cage supporting seat 5 in the extrusion oil film damper, the bearing 4 is in interference fit with a rotor 3 with a balance hole, and the rotor 3 with the balance hole is rotatably connected with the elastic squirrel cage supporting seat through the bearing 4;
step four and step two: adhering a 0-degree damper outer ring support seat cage bar resistance strain gauge 15, a 90-degree damper outer ring support seat cage bar resistance strain gauge 16, a 180-degree damper outer ring support seat cage bar resistance strain gauge 17 and a 270-degree damper outer ring support seat cage bar resistance strain gauge 18 to the damper outer ring support seat cage bar 10 along the circumferential direction, ensuring that the length of the adhering position from the cage bar fixing end is 1/4 of the cage bar length, and monitoring the strain change of the damper outer ring support cage bar 10 in the working process of a rotor;
step four and step three: arranging an X-direction rotor vibration eddy current displacement sensor 27 and a Y-direction rotor vibration eddy current displacement sensor 28 at positions, close to the extrusion damper, of the rotor 3 with the balance holes, wherein the X-direction rotor vibration eddy current displacement sensor 27 and the Y-direction rotor vibration eddy current displacement sensor 28 are arranged at 90 degrees to each other and are used for monitoring radial vibration displacement of the rotor during working;
step four: when the rotor 3 with the balance hole works normally, the strain amplitude of the damper outer ring supporting seat 7 at different rotating speeds is obtained:
εout＝ε(N)； (9)
step four and five: by combining the force transfer coefficient of the damper outer ring supporting seat measured by the experiment, the excitation force transmitted to the damper outer ring supporting seat by the rotor at the rotating speed N of N r/min can be obtained:
Fout|N＝n＝Kout×εout(N＝n)。 (10)
the other components and the connection mode are the same as those of the fourth embodiment.
In the embodiment, the elastic squirrel cage supporting seat 5 is provided with two end sealing grooves, the end sealing ring 6 is arranged on the elastic squirrel cage supporting seat 5, and the end sealing ring 6 is arranged between the elastic squirrel cage supporting seat 5 and the damper outer ring supporting seat 7. .
The sixth specific implementation mode: the present embodiment will be described with reference to fig. 1 to 11, and the present embodiment is further limited to the step five described in the fourth embodiment, and in the present embodiment, the equivalent stiffness K of the oil film in the squeeze film damper in the step five is set0And equivalent damping C0The method is realized by the following steps:
step five, first: when the rotating speed N is N r/min, calculating the vector sum of the force transmitted to the oil film by the elastic squirrel cage supporting seat and the damper outer ring supporting seat as the external force born by the oil film:
Figure BDA0003272463200000111
step five two: the test sensor monitors the vibration displacement of the rotor as x and y, the rotor stably runs when the rotating speed N is N r/min, the precession track of the rotor is a circle, and the radial displacement of the rotor is calculated:
Figure BDA0003272463200000112
step five and step three: analyzing the external force transmission path of the rotor, further obtaining the equivalent dynamic coefficient of the squeeze film damper, and obtaining the equivalent stiffness K when the inner ring of the squeeze film damper performs circular precession when the rotating speed N is N r/min0And equivalent damping C0The coefficient calculation formula is:
Figure BDA0003272463200000121
Figure BDA0003272463200000122
in the formula:
K0the equivalent stiffness of the oil film is N r/min when the rotating speed N is equal to the speed;
C0oil film equivalent damping is achieved when the rotating speed N is N r/min;
Figure BDA0003272463200000123
the oil film force is the oil film force when the rotating speed N is N r/min;
e is the eccentric moment of the rotor in the vortex mode of circular precession;
wherein Ω is the angular frequency of the rotor vortex motion under the vortex motion form of circular precession, and the unit HZ can be calculated by the following formula in the experimental process of the rotor with only unbalanced excitation:
Figure BDA0003272463200000124
the other components and the connection mode are the same as the fifth embodiment mode.
The present invention is not limited to the above embodiments, and any person skilled in the art can make many modifications and equivalent variations by using the above-described structures and technical contents without departing from the scope of the present invention.

Claims (6)

1. A method for identifying dynamics coefficients of an extruded oil film damper is characterized by comprising the following steps: the identification method is realized by the following steps:
the method comprises the following steps: determining elastic squirrel cage bearing seat force transfer coefficient K in squeeze film damperin；
Step two: determining transmission coefficient K of outer ring supporting seat of damper in squeeze film damperout；
Step three: utilizing the force transfer coefficient K of the elastic squirrel cage supporting seat obtained in the step oneinDetermining the excitation force F transmitted by the rotor to the elastic squirrel cage bearing seat when the obtained rotating speed N is N r/minin|N＝n；
Step four: utilizing the force transfer coefficient K of the damper outer ring supporting seat obtained in the step twooutDetermining the excitation force F transmitted by the rotor to the elastic squirrel cage bearing seat when the obtained rotating speed N is N r/minout|N＝n；
Step five: using the rotor obtained in step three when the obtained speed N is N r/minExcitation force F transmitted to elastic squirrel cage supporting seatin|N＝nAnd the excitation force F obtained in the fourth step and transmitted to the elastic squirrel cage supporting seat by the rotor when the obtained rotating speed N is N r/minout|N＝nDetermining the equivalent stiffness K of an oil film in a squeeze film damper0And equivalent damping C0。
2. The method for identifying a squeeze film damper dynamics factor of claim 1 wherein: determining the transmission coefficient K of the elastic squirrel cage supporting seat in the squeeze film damper in the step oneinThe method is realized by the following steps:
the method comprises the following steps: the method comprises the following steps that an elastic squirrel cage supporting seat (5) is installed on a fixing device, an elastic squirrel cage supporting seat bearing plate (19) is installed at an installation seam allowance (5b) of the elastic squirrel cage supporting seat bearing plate on the elastic squirrel cage supporting seat (5) in an interference fit mode, a bearing rod (20) penetrates through a central through hole of the elastic squirrel cage supporting seat bearing plate (19), and the force arms of the bearing rods (20) at two ends of the elastic squirrel cage supporting seat bearing plate (19) are guaranteed to be the same;
the first step is: a first resistance strain gauge measuring terminal (22) is pasted at the position 1/4 where the uppermost cage bar (9) in the elastic cage supporting seat is away from the fixed end of the cage bar by the length of the cage bar, and the first resistance strain gauge measuring terminal (22) is connected into an industrial data acquisition system through a first resistance strain gauge connecting wire (23) and is used for monitoring and recording the strain change of the cage bar in the loading and unloading process;
step one is three: loading and unloading heavy objects at two ends of a bearing rod (20), wherein the two ends of the bearing rod are subjected to three loading-unloading processes in total, and the weight of the heavy objects changed each time is recorded, so that the load change borne by an elastic squirrel cage supporting seat (5) can be obtained;
step one is: fitting according to the loading and unloading process data in the first step and the third step to obtain a force transmission-strain fitting result twice:
Fspring loading＝K1ε1 (1)
FCartridge unloading＝K2ε2 (2)
In the formula:
Fspring loadingStatic load applied to the elastic squirrel cage supporting seat in the loading process;
Fcartridge unloadingStatic load on the elastic squirrel cage supporting seat in the unloading process;
K1the load-strain relation coefficient fitted in the loading process is tested for the static load of the elastic squirrel cage supporting seat;
K2the load-strain relation coefficient fitted in the unloading process is tested for the static load of the elastic squirrel cage supporting seat;
ε1applying a load F for the loading processSpring loading(ii) strain;
ε2applied to the load F for the unloading processCartridge unloading(ii) strain;
step one and five: according to K obtained in the step one or four1And K2Is a reaction of K1And K2Average determination of elastic mouse cage support seat force transfer coefficient K by calculationin：
Figure FDA0003272463190000021
3. The method for identifying a squeeze film damper dynamics factor of claim 2 wherein: determining the force transfer coefficient K of the outer ring supporting seat of the damper in the squeeze film damper in the second stepoutThe method is realized by the following steps:
step two, firstly: installing a damper outer ring supporting seat (7) on a fixing device, installing a damper outer ring supporting seat bearing plate (24) at a damper outer ring supporting seat bearing plate installing seam allowance (7a) on the damper outer ring supporting seat (7) in an interference fit manner, penetrating a bearing rod (20) into a central through hole of the damper outer ring supporting seat bearing plate (24), and ensuring that the force arms of the bearing rods (20) at two ends of the damper outer ring supporting seat bearing plate (24) are the same;
step two: a second resistance strain gauge measuring terminal (25) is pasted on the uppermost cage bar (10) of the damper outer ring supporting seat and at the position 1/4 which is away from the fixed end of the cage bar and has the length of the cage bar as the length of the cage bar, and the second resistance strain gauge measuring terminal (25) is connected into an industrial data acquisition system through a second resistance strain gauge connecting wire (26) and is used for monitoring and recording the strain change of the cage bar in the loading and unloading process;
step two and step three: loading and unloading heavy objects at two ends of a load-bearing rod (20), wherein the two ends of the load-bearing rod are subjected to three loading-unloading processes in total, and the weight of the heavy object changed each time is recorded, so that the load change borne by the damper outer ring supporting seat (7) can be obtained;
step two, four: fitting according to the data of the loading and unloading processes in the second step and the third step to obtain a force transmission-strain fitting result twice:
Fexternal loading＝K3ε3 (4)
FExternal unloading＝K4ε4 (5)
In the formula:
Fexternal loadingStatic load applied to the damper outer ring support seat in the loading process;
Fexternal unloadingStatic load on the damper outer ring supporting seat in the unloading process;
K3the load-strain relation coefficient fitted in the loading process is tested for the static load of the damper outer ring supporting seat;
K4the load-strain relation coefficient fitted in the unloading process is tested for the static load of the damper outer ring supporting seat;
ε3applying a load F for the loading processExternal loading(ii) strain;
ε4applied to the load F for the unloading processExternal unloading(ii) strain;
step two and step five: according to K obtained in the step one or four3And K4Is a reaction of K3And K4Average determination of elastic mouse cage support seat force transfer coefficient K by calculationout：
Figure FDA0003272463190000031
4. The method for identifying a squeeze film damper dynamics factor of claim 3 wherein: in the third step, the force transfer coefficient K of the elastic squirrel cage supporting seat obtained in the first step is utilizedinDetermining the excitation force F transmitted by the rotor to the elastic squirrel cage bearing seat when the obtained rotating speed N is N r/minin|N＝nThe method is realized by the following steps:
step three, firstly: the elastic squirrel cage supporting seat (5) is arranged on a fixing device, a bearing (4) is embedded at a bearing installation seam allowance (5a) on the elastic squirrel cage supporting seat (5), the bearing (4) is in interference fit with a rotor (3) with a balance hole, and the rotor (3) with the balance hole is rotationally connected with the elastic squirrel cage supporting seat through the bearing (4);
step three: adhering a 0-degree elastic squirrel cage supporting cage bar resistance strain gauge (11), a 90-degree elastic squirrel cage supporting cage bar resistance strain gauge (12), a 180-degree elastic squirrel cage supporting cage bar resistance strain gauge (13) and a 270-degree elastic squirrel cage supporting cage bar resistance strain gauge (14) to an elastic squirrel cage supporting seat cage bar (9) along the circumferential direction, ensuring that the length of the adhering position from the cage bar fixing end is 1/4 of the cage bar length, and monitoring the strain change of the elastic squirrel cage supporting cage bar (9) in the working process of a rotor;
step three: when the rotor (3) with the balance hole works normally, the strain amplitude of the elastic squirrel cage supporting seat under different rotating speeds is obtained:
εin＝ε(N)； (7)
step three and four: by combining the force transfer coefficient of the elastic squirrel cage supporting seat measured by the experiment, the excitation force transmitted to the elastic squirrel cage supporting seat by the rotor at the rotating speed N of N r/min can be obtained:
Fin|N＝n＝Kin×εin(N＝n)。 (8)
5. identification of a squeeze film damper dynamics coefficient according to claim 4The method is characterized in that: in the fourth step, the force transfer coefficient K of the damper outer ring supporting seat obtained in the second step is utilizedoutDetermining the excitation force F transmitted by the rotor to the outer ring bearing seat of the damper when the obtained rotating speed N is N r/minout|N＝nThe method is realized by the following steps:
step four, firstly: installing an extrusion oil film damper on a fixing device, wherein the extrusion oil film damper comprises an elastic squirrel cage supporting seat (5), an extrusion oil film damper end sealing ring (6) and a damper outer ring supporting seat (7), the extrusion oil film damper end sealing ring (6) is arranged between the elastic squirrel cage supporting seat (5) and the damper outer ring supporting seat (7), so that an extrusion oil film is formed between the elastic squirrel cage supporting seat (5) and the damper outer ring supporting seat (7), a bearing (4) is embedded at a bearing installation spigot (5a) on the elastic squirrel cage supporting seat (5) in the extrusion oil film damper, the bearing (4) is in interference fit with a rotor (3) with a balance hole, and the rotor (3) with the balance hole is rotationally connected with the elastic squirrel cage supporting seat through the bearing (4);
step four and step two: adhering a 0-degree damper outer ring supporting seat cage bar resistance strain gauge (15), a 90-degree damper outer ring supporting seat cage bar resistance strain gauge (16), a 180-degree damper outer ring supporting seat cage bar resistance strain gauge (17) and a 270-degree damper outer ring supporting seat cage bar resistance strain gauge (18) to the damper outer ring supporting seat cage bar (10) along the circumferential direction, ensuring that the length of the adhering position from the fixed end of the cage bar is 1/4 of the length of the cage bar, and monitoring the strain change of the damper outer ring supporting cage bar (10) in the working process of a rotor;
step four and step three: arranging an X-direction rotor vibration eddy current displacement sensor (27) and a Y-direction rotor vibration eddy current displacement sensor (28) at the position, close to the extrusion damper, of a rotor (3) with a balance hole, wherein the X-direction rotor vibration eddy current displacement sensor (27) and the Y-direction rotor vibration eddy current displacement sensor (28) are arranged at an angle of 90 degrees with each other and are used for monitoring radial vibration displacement of the rotor during working;
step four: when the rotor (3) with the balance hole works normally, the strain amplitude of the damper outer ring supporting seat (7) at different rotating speeds is obtained:
εout＝ε(N)； (9)
step four and five: by combining the force transfer coefficient of the damper outer ring supporting seat measured by the experiment, the excitation force transmitted to the damper outer ring supporting seat by the rotor at the rotating speed N of N r/min can be obtained:
Fout|N＝n＝Kout×εout(N＝n)。 (10)
6. the method for identifying a squeeze film damper dynamics factor of claim 5 wherein: the equivalent rigidity K of the oil film in the squeeze film damper in the step five0And equivalent damping C0The method is realized by the following steps:
step five, first: when the rotating speed N is N r/min, calculating the vector sum of the force transmitted to the oil film by the elastic squirrel cage supporting seat and the damper outer ring supporting seat as the external force born by the oil film:
Figure FDA0003272463190000051
step five two: the test sensor monitors the vibration displacement of the rotor as x and y, the rotor stably runs when the rotating speed N is N r/min, the precession track of the rotor is a circle, and the radial displacement of the rotor is calculated:
Figure FDA0003272463190000052
step five and step three: analyzing the external force transmission path of the rotor, further obtaining the equivalent dynamic coefficient of the squeeze film damper, and obtaining the equivalent stiffness K when the inner ring of the squeeze film damper performs circular precession when the rotating speed N is N r/min0And equivalent damping C0The coefficient calculation formula is:
Figure FDA0003272463190000053
Figure FDA0003272463190000054
in the formula:
K0the equivalent stiffness of the oil film is N r/min when the rotating speed N is equal to the speed;
C0oil film equivalent damping is achieved when the rotating speed N is N r/min;
Figure FDA0003272463190000055
the oil film force is the oil film force when the rotating speed N is N r/min;
e is the eccentric moment of the rotor in the vortex mode of circular precession;
wherein Ω is the angular frequency of the rotor vortex motion under the vortex motion form of circular precession, and the unit HZ can be calculated by the following formula in the experimental process of the rotor with only unbalanced excitation:
Figure FDA0003272463190000056
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