CN110926810A - Ultrasonic radial bearing friction torque and high-speed running stability testing device - Google Patents
Ultrasonic radial bearing friction torque and high-speed running stability testing device Download PDFInfo
- Publication number
- CN110926810A CN110926810A CN201911093077.7A CN201911093077A CN110926810A CN 110926810 A CN110926810 A CN 110926810A CN 201911093077 A CN201911093077 A CN 201911093077A CN 110926810 A CN110926810 A CN 110926810A
- Authority
- CN
- China
- Prior art keywords
- bearing
- rotor
- friction torque
- motor
- laser displacement
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M13/00—Testing of machine parts
- G01M13/04—Bearings
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01B—MEASURING LENGTH, THICKNESS OR SIMILAR LINEAR DIMENSIONS; MEASURING ANGLES; MEASURING AREAS; MEASURING IRREGULARITIES OF SURFACES OR CONTOURS
- G01B11/00—Measuring arrangements characterised by the use of optical techniques
- G01B11/02—Measuring arrangements characterised by the use of optical techniques for measuring length, width or thickness
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
- G01L5/0009—Force sensors associated with a bearing
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Abstract
The invention discloses a device for testing friction torque and high-speed running stability of an ultrasonic radial bearing, and relates to a method for measuring the running stability of the friction torque of the ultrasonic radial bearing during high-speed running. According to the current feedback method, the friction torque of the bearing during high-speed operation can be calculated through the current value output by the current detection port of the motor driver. By means of the laser displacement sensors arranged in the horizontal and vertical directions, a track diagram of the center of the bearing rotor can be measured. By utilizing a short-time Fourier transform method, a joint time-frequency spectrogram of the center track of the bearing rotor can be obtained, and then the high-speed running stability of the ultrasonic bearing rotor is judged. The invention adopts the xPC-Target system in the process of controlling the rotating speed of the rotor and measuring the load current of the motor, thereby ensuring the real-time performance of the control and data acquisition process. The method is used for measuring the friction torque of the ultrasonic radial bearing during high-speed operation and judging the stability of the bearing support rotor during high-speed operation.
Description
Technical Field
The invention belongs to the technical field of bearing performance testing, and particularly relates to a device for testing friction torque and high-speed running stability of an ultrasonic radial bearing.
Background
The magnitude and the fluctuation of the friction torque of the ultrasonic bearing have important influence on the dynamic characteristics and the running precision of the bearing. As a non-contact bearing using air as a working medium, an ultrasonic bearing exhibits different frictional characteristics in a high-speed operation stage than in a low-speed operation stage. By using a current feedback method, the friction torque of the ultrasonic bearing under different working conditions can be measured, and the rule of the influence of the rotating speed of the bearing on the friction torque is obtained. When the bearing runs at a high speed, the running stability of the bearing is influenced by factors such as dynamic unbalance of a rotor, bearing installation precision, air film oscillation and the like. When the bearing-rotor system is unstable, the outer circle of the rotor collides or scrapes with the inner ring of the bearing, so that the bearing is damaged. Time-frequency spectrum analysis of the axis locus of the rotor is an effective method for judging whether the bearing rotor system is unstable or not. A bearing high-speed operation stability experiment testing system is built, the eccentric amplitude or time frequency spectrum of the rotor axis of the bearing rotor in the starting, stopping and speed increasing and reducing processes is obtained, and the operation stability of the bearing rotor system can be described. In the bearing operation process, the rotor speed, the suspension load and the bearing clearance are key factors influencing the bearing operation stability. Through experimental means, the influence rule of the three on the high-speed running stability of the bearing is analyzed, and measures for enhancing the high-speed running stability of the bearing can be explored.
Disclosure of Invention
In order to solve the problems in the prior art, the invention provides a system for measuring the friction torque and the high-speed running stability of an ultrasonic radial bearing, the resolution of the friction torque of the device is 0.8 micro Newton meter, and the high-speed running stability of a rotor below 60000 r/min can be measured.
In order to achieve the purpose, the invention adopts the technical scheme that:
a device for testing the friction torque and high-speed running stability of an ultrasonic radial bearing comprises a vibration isolation platform, a closed cover, a bearing rotor system, an axis track measuring system and a data acquisition and control system, wherein the closed cover covers the bearing rotor system arranged on the vibration isolation platform,
the bearing rotor system comprises three piezoelectric transducers, a bearing shell, a rotor, a motor and a flexible coupling, wherein the motor drives the rotor to rotate at a high speed through the flexible coupling;
the axis track measuring system comprises a laser displacement sensor which is horizontally arranged and used for measuring the horizontal eccentric distance of the overhanging end of the rotor, a laser displacement sensor controller and a computer, wherein the laser displacement sensor which is vertically arranged and used for measuring the vertical eccentric distance of the overhanging end of the rotor is positioned in a closed cover;
the data acquisition and control system comprises an upper computer and a lower computer which are communicated with each other, wherein a data acquisition card is installed on the lower computer, the data acquisition card is connected with a motor driver, and the motor driver is connected with a driving motor.
As a preferred scheme, the bearing rotor system further comprises a motor support and a bearing support, the motor support supports the motor, the bottom of the bearing support is fixed on the vibration isolation platform, and the bearing support supports the bearing shell.
Preferably, the cooling fan is fixed on a bearing shell at the tail end of the piezoelectric transducer through a fan support.
Preferably, the controller of the laser displacement sensor is connected with a controller power supply.
As a preferred scheme, the axle center trajectory measurement system further comprises a universal magnetic meter base, the universal magnetic meter base is adsorbed on the vibration isolation platform, the universal magnetic meter base is respectively connected with a laser displacement sensor through a laser displacement sensor mounting plate, and the laser displacement sensor, the laser displacement sensor mounting plate and the universal magnetic meter base are also covered by the closed cover.
As a preferred scheme, an interface board is arranged between the data acquisition card and the motor driver, the data acquisition card and the interface board are connected through an acquisition card cable, and the motor driver is connected with a direct current power supply.
As a preferred scheme, the upper computer and the lower computer are connected and communicated through an Ethernet communication cable, the upper computer is connected with an upper computer display, and the lower computer is connected with a lower computer display.
As a preferred scheme, the closed cover is connected with the vibration isolation platform through bolts, and closed cover wire outlet holes are formed in the top of the closed cover and the position close to the installation plane according to the wiring design requirement; for convenient observation and certain intensity assurance, the material of airtight cover is transparent organic glass. The closed cover has two functions: firstly, the bearing is prevented from being influenced by external airflow disturbance when working; and secondly, safety is ensured to prevent the rotor which runs at high speed in the experimental process from flying out to cause accidents.
Preferably, the fan support and the heat-reducing fan and the fan support and the bearing shell are connected through bolts.
As a preferred scheme, grid holes are formed in the front side and the back side of the fan support, fan support wire outlet holes are formed in the side wall of the fan support, the grid holes are designed to facilitate heat dissipation, and the fan support wire outlet holes facilitate power supply and wiring of the transducer.
Compared with the prior art, the invention has the following beneficial effects:
1. the invention has scientific and reasonable structural design and measurement scheme, the motor control system controls the rotating speed of the rotor, the motor driver monitoring port acquires current data, and the bearing friction torque is calculated; and monitoring the central track data of the rotor by a high-precision laser displacement sensor, and judging the stability of the bearing in high-speed operation by a Simulink real-time toolbox in MATLAB software. The invention has two functions of measuring the friction torque of the bearing and testing the stability.
2. The invention can realize the radial high-speed friction torque and running stability test of the ultrasonic bearing, and has simple control system and strong flexibility.
3. The vibration isolation device has the advantages of being safe, reliable, good in real-time performance and simple in measurement principle, and is suitable for being popularized and used.
Drawings
FIG. 1 is an assembly schematic of the present invention;
FIG. 2 is a perspective view of the bearing rotor system of the present invention;
FIG. 3 is a front view of the bearing rotor system of the present invention;
FIG. 4 is a top view of the bearing rotor system of the present invention;
FIG. 5 is a side view of the bearing rotor system of the present invention;
FIG. 6 is a measurement schematic of the present invention;
FIG. 7 is a schematic view of the mounting location of the laser displacement sensor of the present invention;
FIG. 8 is a schematic vibration diagram of the present invention;
FIG. 9 is a schematic diagram of the measurement of the no-load friction torque of the motor in the present invention;
fig. 10 is a schematic diagram of the measurement of the motor load friction torque in the invention.
Detailed Description
The present invention will be further described with reference to the following examples.
As shown in fig. 1-5, an ultrasonic radial bearing friction torque and high-speed operation stability testing device comprises a vibration isolation platform 1, a closed cover 2, a bearing rotor system 3, an axis locus measuring system 4 and a data acquisition and control system 5, wherein the closed cover 2 covers the bearing rotor system 3 mounted on the vibration isolation platform 1,
the closed cover 2 is connected with the vibration isolation platform 1 through bolts, closed cover wire outlet holes 2-1 are formed in the top of the closed cover 2 and the position close to the installation plane according to wiring design requirements, data lines of the laser displacement sensor 4-1, power supply lines of the motor 3-13 and connecting lines of the motor driver 5-9 penetrate through the closed cover wire outlet holes 2-1; for convenient observation and certain intensity assurance, the material of sealed cover 2 is transparent organic glass. The closed cover has two functions: firstly, the bearing is prevented from being influenced by external airflow disturbance when working; secondly, safety is guaranteed, so that accidents caused by flying-out of a rotor which runs at high speed in the experimental process are prevented;
the bearing rotor system 3 comprises three piezoelectric transducers 3-1, a bearing shell 3-4, a rotor 3-11, a motor 3-13 and a flexible coupling 3-14, wherein the motor 3-13 drives the rotor 3-11 to rotate at a high speed through the flexible coupling 3-14, the three piezoelectric transducers 3-1 are arranged on the circumference of the rotor 3-11, the three piezoelectric transducers 3-1 are positioned in the bearing shell 3-4, and the tail end of each piezoelectric transducer 3-1 is correspondingly provided with a heat reduction fan 3-3; the bearing rotor system 3 further comprises a motor support 3-12 and a bearing support 3-15, the motor support 3-12 supports a motor 3-13, the bottom of the bearing support 3-15 is fixed on the vibration isolation platform 1, a bearing shell 3-4 is supported on the bearing support 3-15, and the cooling fan 3-3 is fixed on the bearing shell 3-4 at the tail end of the piezoelectric transducer 3-1 through a fan support 3-2; the three piezoelectric transducers have the same structural composition and design size, and the concave cylindrical surfaces at the tail ends of the three piezoelectric transducers form complete circumferential envelope on the rotor in the circumferential direction; in order to ensure the coaxiality between a motor shaft of the motor 3-13 and the rotor 3-11 and the assembly precision between the rotor and the bearing hole, seam allowance structures are processed between the motor 3-13 and the motor bracket 3-12 and between the motor bracket 3-12 and the bearing shell 3-4; the fan support 3-2 and the heat-reducing fan 3-3 are connected through bolts, and the fan support 3-2 and the bearing shell 3-4 are connected through bolts; grid holes 3-16 are formed in the front side and the back side of the fan support 3-2, fan support outlet holes 3-17 are formed in the side wall of the fan support 3-2, the grid holes 3-16 are designed to facilitate heat dissipation, and the fan support outlet holes 3-17 facilitate power supply and wiring of a piezoelectric transducer; the motors 3-13 are started, and the rotors 3-11 are driven to rotate at a high speed through the flexible couplings 3-14. The ultrasonic bearing supports the rotor. During excitation, three paths of high-frequency voltage signals can be sent out by a three-channel signal generator, and the voltage signals are respectively output to the three piezoelectric transducers after being subjected to amplitude amplification by a three-channel driving amplifier. After receiving the excitation of the voltage signal of ultrasonic frequency, the piezoelectric transducer generates acoustic radiation force to carry out suspension support on the bearing rotor in high-speed operation. When the piezoelectric transducer generates heat seriously, the cooling fan is started to work, heat is emitted outwards from the inside of the bearing, and the bearing is ensured to work normally and stably. When the flexible coupling is selected, on the basis of ensuring the rotation precision of the coupling, the radial and axial sizes of the coupling are required to be as small as possible, and the flexibility of the coupling in the radial direction is required to be as large as possible. When the motor is selected, the motor is guaranteed to have a rated rotating speed of more than 50000 r/min, and a motor driver has enough high current resolution.
The axis track measuring system 4 comprises a horizontally arranged laser displacement sensor 4-1 for measuring the horizontal eccentric distance of the overhanging end of the rotor 3-11, a vertically arranged laser displacement sensor 4-1 for measuring the vertical eccentric distance of the overhanging end of the rotor 3-11, a laser displacement sensor controller 4-4 and a computer 4-6, wherein the laser displacement sensor 4-1 is positioned in the closed cover 2, a laser light source of the laser displacement sensor 4-1 vertically hits on a bus of the overhanging end of the rotor 3-11, and the laser displacement sensor 4-1, the laser displacement sensor controller 4-4 and the computer 4-6 are sequentially connected; the laser displacement sensor controller 4-4 is connected with a controller power supply 4-5; the axis track measuring system 4 further comprises a universal magnetic meter seat 4-3, the universal magnetic meter seat 4-3 is adsorbed on the vibration isolation platform 1, and the universal magnetic meter seat 4-3 is respectively connected with a laser displacement sensor 4-1 through a laser displacement sensor mounting plate 4-2; when the laser displacement sensor is used, the light source of the laser displacement sensor 4-1 is adjusted, so that emitted laser vertically hits on a bus of the extending end of the rotor 3-11. And adjusting the distance between the laser source and the outer circle surface of the rotor to enable the laser emission distance to be within the measurement requirement range, horizontally placing one laser displacement sensor 4-1 to measure the horizontal eccentric distance of the extending end of the rotor 3-11, vertically placing the other laser displacement sensor 4-1 to measure the vertical eccentric distance of the extending end of the rotor 3-11. As shown in fig. 6, the ultrasonic bearings are mounted on the periphery of the rotors 3-11, and the positions of the two rotors are plotted in fig. 6, wherein one position is a position where the rotor axis coincides with the bearing centerline; the other position is a position where the rotor axis is deviated from the bearing center (the rotor is in an eccentric state), in which: l is1Is the horizontal distance, L, from the left end of the rotor to the center of the bearing2Is the total length of the rotor, delta is the vertical distance between the center of the eccentric rotor and the center of the bearing, and delta isAnd calculating the vertical distance between the right end of the eccentric rotor and the center of the bearing according to the geometric relationship, wherein the eccentric distance of the center of the bearing rotor 3-11 is calculated.
The data acquisition and control system 5 comprises an upper computer 5-3 and a lower computer 5-1 which are connected through an Ethernet communication cable 5-5 and are communicated with each other, the upper computer 5-3 is connected with an upper computer display 5-4, the lower computer 5-1 is connected with a lower computer display 5-2, a data acquisition card 5-6 is installed on the lower computer 5-1, the data acquisition card 5-6 is connected with a motor driver 5-9, and the motor driver 5-9 is connected with a driving motor 3-13. In order to facilitate the connection, an interface board 5-8 is arranged between a data acquisition card 5-6 and a motor driver 5-9, the data acquisition card 5-6 is connected with the interface board 5-8 through an acquisition card cable 5-7, and the motor driver 5-9 is connected with a direct current power supply 5-10; the rotation speed control and the current detection of the motor 3-13 are completed by the cooperation of the upper computer 5-3 and the lower computer 5-1. The upper computer is provided with a control program and a monitoring program, and the lower computer is provided with a data acquisition card 5-6. The lower computer collects the monitoring parameters of the motor drivers 5-9 in real time and uploads the parameters to the upper computer. The upper computer sends the control instruction to the lower computer in real time and the control instruction is transmitted to the motor driver by the lower computer.
The principle of the invention is as follows:
(1) and the principle of the ultrasonic bearing operation stability test is explained by combining the following steps of FIG. 9 and FIG. 10:
firstly, the ultrasonic bearing is started to work, and bearing control parameters are adjusted to enable the bearing to work in a good stable state. At this time, the bearing rotor is suspended in the bearing center. Then, the motor is started, and the rotating speed of the motor is fixed at a certain rotating speed value or moves according to a set rotating speed curve by adjusting the control parameters of the rotating speed of the motor in the upper computer program. And starting the laser displacement sensor, and recording the eccentricity of the overhanging end of the bearing rotor in the horizontal and vertical directions respectively. The eccentric distance of the center of the bearing rotor is converted by the geometrical relationship shown in fig. 3, and the eccentric track of the bearing rotor is obtained. And drawing a three-dimensional time-frequency spectrogram of the eccentric track data of the bearing rotor on a computer, and judging the rotation stability of the bearing rotor.
(2) And the principle of measuring the radial friction torque of the ultrasonic bearing is explained by combining the following steps of FIG. 9 and FIG. 10:
a. the flexible coupling is disconnected from the bearing rotor, the motor is started, and the rotating speed of the motor is fixed at a certain rotating speed value or moves according to a certain set rotating speed curve by adjusting the control parameters of the rotating speed of the motor in the program of the upper computer. And recording the current value of the motor coil when the motor is in no-load in real time through an upper computer system and a lower computer system, and converting the no-load friction torque of the motor.
b. The flexible coupling is connected with the bearing rotor, the ultrasonic bearing is started to work, and the bearing control parameters are adjusted, so that the bearing works in a good stable state. And starting the motor, and enabling the rotating speed of the motor to be fixed at a certain rotating speed value or move according to a certain set rotating speed curve by adjusting the control parameters of the rotating speed of the motor in the upper computer program. And recording the current value of the motor coil when the motor is loaded in real time through an upper computer system and a lower computer system, and converting the friction torque of the motor when the motor is loaded.
and the absolute value of the difference value of the two measured torque values of the a and the b is the bearing friction torque value.
According to the current feedback method, the friction torque of the bearing during high-speed operation can be calculated through the current value output by the current detection port of the motor driver. By means of the laser displacement sensors arranged in the horizontal and vertical directions, a track diagram of the center of the bearing rotor can be measured. By utilizing a short-time Fourier transform method, a joint time-frequency spectrogram of the center track of the bearing rotor can be obtained, and then the high-speed running stability of the ultrasonic bearing rotor is judged. The invention adopts the xPC-Target system in the process of controlling the rotating speed of the rotor and measuring the load current of the motor, thereby ensuring the real-time performance of the control and data acquisition process. The method is used for measuring the friction torque of the ultrasonic radial bearing during high-speed operation and judging the stability of the bearing support rotor during high-speed operation.
The above description is only of the preferred embodiments of the present invention, and it should be noted that: it will be apparent to those skilled in the art that various modifications and adaptations can be made without departing from the principles of the invention and these are intended to be within the scope of the invention.
Claims (10)
1. The utility model provides an supersound journal bearing friction torque and high-speed operation stability testing arrangement which characterized in that: comprises a vibration isolation platform (1), a closed cover (2), a bearing rotor system (3), an axis track measuring system (4) and a data acquisition and control system (5), wherein the closed cover (2) covers the bearing rotor system (3) arranged on the vibration isolation platform (1),
the bearing rotor system (3) comprises three piezoelectric transducers (3-1), a bearing shell (3-4), a rotor (3-11), a motor (3-13) and a flexible coupling (3-14), the motor (3-13) drives the rotor (3-11) to rotate through the flexible coupling (3-14), the three piezoelectric transducers (3-1) are installed on the circumference of the rotor (3-11), the three piezoelectric transducers (3-1) are located in the bearing shell (3-4), and the tail end of each piezoelectric transducer (3-1) is correspondingly provided with a cooling fan (3-3);
the axis track measuring system (4) comprises a laser displacement sensor (4-1) which is horizontally arranged and used for measuring the horizontal eccentric distance of the extending end of the rotor (3-11), a laser displacement sensor (4-1) which is vertically arranged and used for measuring the vertical eccentric distance of the extending end of the rotor (3-11), a laser displacement sensor controller (4-4) and a computer (4-6), wherein the laser displacement sensor (4-1) is positioned in the closed cover (2), a laser light source of the laser displacement sensor (4-1) vertically hits a bus of the extending end of the rotor (3-11), and the laser displacement sensor (4-1), the laser displacement sensor controller (4-4) and the computer (4-6) are sequentially connected;
the data acquisition and control system (5) comprises an upper computer (5-3) and a lower computer (5-1) which are communicated with each other, wherein a data acquisition card (5-6) is installed on the lower computer (5-1), the data acquisition card (5-6) is connected with a motor driver (5-9), and the motor driver (5-9) is connected with a driving motor (3-13).
2. The ultrasonic radial bearing friction torque and high-speed operation stability testing device according to claim 1, characterized in that: the bearing rotor system (3) further comprises a motor support (3-12) and a bearing support (3-15), the motor support (3-12) supports the motor (3-13), the bottom of the bearing support (3-15) is fixed on the vibration isolation platform (1), and the bearing support (3-15) supports the bearing shell (3-4).
3. The ultrasonic radial bearing friction torque and high-speed operation stability testing device according to claim 1, characterized in that: the cooling fan (3-3) is fixed on a bearing shell (3-4) at the tail end of the piezoelectric transducer (3-1) through a fan support (3-2).
4. The ultrasonic radial bearing friction torque and high-speed operation stability testing device according to claim 1, characterized in that: the laser displacement sensor controller (4-4) is connected with a controller power supply (4-5).
5. The ultrasonic radial bearing friction torque and high-speed operation stability testing device according to claim 4, wherein: the axis track measuring system (4) further comprises a universal magnetic gauge stand (4-3), the universal magnetic gauge stand (4-3) is adsorbed on the vibration isolation platform (1), and the universal magnetic gauge stand (4-3) is connected with a laser displacement sensor (4-1) through a laser displacement sensor mounting plate (4-2).
6. The ultrasonic radial bearing friction torque and high-speed operation stability testing device according to claim 1, characterized in that: an interface board (5-8) is arranged between the data acquisition card (5-6) and the motor driver (5-9), the data acquisition card (5-6) is connected with the interface board (5-8) through an acquisition card cable (5-7), and the motor driver (5-9) is connected with a direct current power supply (5-10).
7. The ultrasonic radial bearing friction torque and high-speed operation stability testing device according to claim 1, characterized in that: the upper computer (5-3) and the lower computer (5-1) are connected and communicated through an Ethernet communication cable (5-5), the upper computer (5-3) is connected with an upper computer display (5-4), and the lower computer (5-1) is connected with a lower computer display (5-2).
8. The ultrasonic radial bearing friction torque and high-speed operation stability testing device according to claim 1, characterized in that: the closed cover (2) is connected with the vibration isolation platform (1) through bolts, and closed cover wire outlet holes (2-1) are formed in the top of the closed cover (2) and the position close to the installation plane according to wiring design requirements; the material of the closed cover (2) is transparent organic glass.
9. The ultrasonic radial bearing friction torque and high-speed operation stability testing device according to claim 3, wherein: the fan support (3-2) and the heat-reducing fan (3-3) and the fan support (3-2) and the bearing shell (3-4) are connected through bolts.
10. The ultrasonic radial bearing friction torque and high-speed operation stability testing device according to claim 3, wherein: grid holes (3-16) are formed in the front face and the back face of the fan support (3-2), and fan support outlet holes (3-17) are formed in the side wall of the fan support (3-2).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911093077.7A CN110926810A (en) | 2019-11-11 | 2019-11-11 | Ultrasonic radial bearing friction torque and high-speed running stability testing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911093077.7A CN110926810A (en) | 2019-11-11 | 2019-11-11 | Ultrasonic radial bearing friction torque and high-speed running stability testing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110926810A true CN110926810A (en) | 2020-03-27 |
Family
ID=69853698
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911093077.7A Pending CN110926810A (en) | 2019-11-11 | 2019-11-11 | Ultrasonic radial bearing friction torque and high-speed running stability testing device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN110926810A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114046979A (en) * | 2021-11-16 | 2022-02-15 | 珠海格力电器股份有限公司 | Compressor rotor track testing device and method and compressor system |
| CN114544174A (en) * | 2022-02-14 | 2022-05-27 | 浙江工业大学 | Ultrasonic suspension bearing capacity testing device |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009243908A (en) * | 2008-03-28 | 2009-10-22 | Takata Corp | Abnormality diagnosis method of low-speed rotary machine |
| CN106644475A (en) * | 2016-10-12 | 2017-05-10 | 河南科技大学 | Static and dynamic characteristics and stability test method for micro gas bearing |
| CN107269697A (en) * | 2017-07-07 | 2017-10-20 | 哈尔滨工业大学 | It is a kind of to bear the ultrasound suspending bearing of radial and axial load simultaneously |
| CN109060210A (en) * | 2018-09-03 | 2018-12-21 | 北京控制工程研究所 | A kind of bearing frictional torque measurement method and system based on piezoelectric ceramics |
| CN109781413A (en) * | 2019-03-06 | 2019-05-21 | 西北工业大学 | A kind of high-precision rolling bearing retainer stability test device and method |
-
2019
- 2019-11-11 CN CN201911093077.7A patent/CN110926810A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009243908A (en) * | 2008-03-28 | 2009-10-22 | Takata Corp | Abnormality diagnosis method of low-speed rotary machine |
| CN106644475A (en) * | 2016-10-12 | 2017-05-10 | 河南科技大学 | Static and dynamic characteristics and stability test method for micro gas bearing |
| CN107269697A (en) * | 2017-07-07 | 2017-10-20 | 哈尔滨工业大学 | It is a kind of to bear the ultrasound suspending bearing of radial and axial load simultaneously |
| CN109060210A (en) * | 2018-09-03 | 2018-12-21 | 北京控制工程研究所 | A kind of bearing frictional torque measurement method and system based on piezoelectric ceramics |
| CN109781413A (en) * | 2019-03-06 | 2019-05-21 | 西北工业大学 | A kind of high-precision rolling bearing retainer stability test device and method |
Non-Patent Citations (2)
| Title |
|---|
| 李贺: ""具有径向和轴向复合承载能力的超声悬浮轴承特性研究"", 《中国博士学位论文全文数据库 工程科技Ⅱ辑 （月刊 ）机械工业》 * |
| 滑宇翔: ""超声悬浮轴承径向承载特性分析及实验研究"", 《中国优秀硕士学位论文全文数据库 工程科技Ⅱ辑 （月刊）机械工业》 * |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114046979A (en) * | 2021-11-16 | 2022-02-15 | 珠海格力电器股份有限公司 | Compressor rotor track testing device and method and compressor system |
| CN114046979B (en) * | 2021-11-16 | 2022-11-18 | 珠海格力电器股份有限公司 | Compressor rotor track testing device and method and compressor system |
| CN114544174A (en) * | 2022-02-14 | 2022-05-27 | 浙江工业大学 | Ultrasonic suspension bearing capacity testing device |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN109061471B (en) | Electromagnetic compatibility dynamometer testing system for electric automobile motor | |
| CN103698128B (en) | A kind of air gaps hybrid magnetic suspension bearing performance testing device | |
| CN110926810A (en) | Ultrasonic radial bearing friction torque and high-speed running stability testing device | |
| KR20140024891A (en) | Rotational torsion tester | |
| CN109029988A (en) | Multifunction flexible gearbox test macro | |
| CN110567660B (en) | Unbalance excitation test bed for elastic support rotor system and method for measuring rigidity of elastic ring of unbalance excitation test bed | |
| CN109855828B (en) | Bolt group connection vibration reliability experiment device and test method | |
| CN107328506A (en) | High-speed electric main shaft dynamometer machine and its application | |
| CN209131969U (en) | Multifunction flexible gearbox test macro | |
| CN113765301B (en) | Magnetic suspension motor and method for improving dynamic balance debugging accuracy | |
| CN106768752B (en) | A kind of centrifugal pump is interior to flow excited vibration separator and test method | |
| CN103791819B (en) | Aeroengine rotor assembly method and the device of swivel angle plate is adjusted based on regulation of mental activities | |
| CN103487182B (en) | High-accuracy measuring method and device for high-speed rotor flow resistance torque | |
| CN208860610U (en) | A kind of automotive hub bearing dynamic vibration durable test stand | |
| CN209838604U (en) | Wind turbine blade stress-strain testing device based on rotating platform | |
| CN210221391U (en) | Dynamic balancing machine suitable for self-driven impeller rotor | |
| CN110057580B (en) | Device and method for testing dynamic response characteristics of main shaft of elevator | |
| CN110631818A (en) | New forms of energy electric motor rotor overspeed testing arrangement | |
| CN109696286A (en) | A kind of high-speed electric main shaft dynamically load vibration measurement device | |
| CN101576367A (en) | Rotor measuring device of large vertical water turbine generator | |
| CN110487541B (en) | Performance testing device and method for air floatation main shaft | |
| CN213812681U (en) | Motor static friction moment testing device | |
| CN107300447A (en) | A kind of flabellum single-side dynamic balance machine | |
| CN220893776U (en) | Test bench for bearing test | |
| CN202794220U (en) | Sensor testing device of engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20200327 |
|
| RJ01 | Rejection of invention patent application after publication |