CN114018802A - Measuring system and calculating method for friction coefficient of flow distribution pair of plunger pump - Google Patents
Measuring system and calculating method for friction coefficient of flow distribution pair of plunger pump Download PDFInfo
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- CN114018802A CN114018802A CN202111150142.2A CN202111150142A CN114018802A CN 114018802 A CN114018802 A CN 114018802A CN 202111150142 A CN202111150142 A CN 202111150142A CN 114018802 A CN114018802 A CN 114018802A
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- G01N19/02—Measuring coefficient of friction between materials
Abstract
The invention discloses a measuring system and a friction coefficient calculation method of a flow distribution pair, wherein the measuring system is applied to a flow distribution pair test bed based on a high-speed high-pressure axial plunger pump, the measuring system comprises a torque and rotating speed sensor, a rotating speed and torque digital display meter, two pressure sensors, four temperature sensors, two frequency digital display meters, a data acquisition board card, a computer and a data acquisition system, the data acquisition board card sends measuring data to the computer, the data acquisition system is used for storing and calculating the friction coefficient, and the friction coefficient calculation method comprises the following steps: initializing a sensor and a digital display meter, and starting data acquisition; secondly, analyzing the stress of the friction testing device of the flow distribution pair; step three, obtaining a friction coefficient expression of the flow distribution pair; step four, obtaining test parameters under different working conditions; step five, the friction coefficient of the flow distribution pair under different working conditions is obtained, and the beneficial effects are that: the method for effectively calculating the friction coefficient of the flow distribution pair is simple, convenient and accurate to calculate and wide in measuring working condition range.
Description
Technical Field
The invention relates to a method for measuring and calculating a friction coefficient of a flow distribution pair of a plunger pump, in particular to a measuring system and a method for calculating the friction coefficient of the flow distribution pair of an axial plunger pump, and belongs to the field of hydraulic experiments.
Background
With the pressure grade of modern airplanes rising, plunger pumps for aviation EHA are continuously developing towards high speed and high pressure. The friction pair design of the plunger pump is challenged by the working conditions of high speed and high pressure, and the volume efficiency and the mechanical efficiency of the plunger pump are greatly determined by the key friction pair. The friction pair of the plunger pump mainly comprises a plunger pair, a sliding shoe pair and a flow distribution pair. The most critical friction pair in the plunger pump plays a decisive role in the service life of the pump, so that the tribological characteristics of the flow distribution pair are urgently needed to be researched.
In order to solve the problems and obtain the friction coefficient of the flow distribution pair, a measurement system and a calculation method of the friction coefficient of the flow distribution pair need to be developed, in the patents which are already put into use and disclosed or authorized, a test bed is built around the structure of the flow distribution pair, and a more scientific method for calculating the friction coefficient is not provided. Aiming at the problem, the invention builds a specific measuring system based on a high-speed high-pressure axial plunger pump flow distribution pair test device, collects and stores experimental data through a sensor group and a data collection board card, and provides a flow distribution pair friction coefficient calculation method.
Disclosure of Invention
Aiming at the research requirements of the friction characteristics of the flow distribution pair of the existing axial plunger pump, the invention provides a parameter measuring system and a flow distribution pair friction coefficient calculating method which can be used on a high-speed high-pressure axial plunger pump flow distribution pair testing device.
The invention is realized by the following technical scheme: a measuring system and a calculating method for friction coefficients of a plunger pump flow distribution pair comprise a hydraulic-mechanical system for a flow distribution pair test device, two pressure sensors, a frequency digital display meter corresponding to the pressure sensors, a torque rotating speed sensor and a torque rotating speed digital display meter corresponding to the torque rotating speed sensor, four temperature sensors, a sublimation data acquisition board card, a computer and a self-developed upper computer data acquisition system. The number of the sensors is consistent with the number of the data input ports of the data acquisition board card, the data output of the porphyry data acquisition board card is transmitted to the computer through the USB interface, and an upper computer data acquisition system of the computer dynamically displays the data and generates a report for storage.
Furthermore, the hydraulic-mechanical system for the flow distribution pair test device comprises a constant pressure pump station, an energy accumulator, an unloading overflow valve, a proportional pressure reducing valve, an electromagnetic directional valve and a servo motor. The constant pressure pump station is used for providing constant pressure oil for the hydraulic system, the energy accumulator is used for maintaining pressure of the hydraulic system, and the unloading overflow valve is used for adjusting the pressure of the system and simulating the pressure of a high-pressure cavity of the plunger pump. The pressure reducing valve is used for adjusting the pressure of the loading piston and simulating the pressing force applied to the cylinder body of the plunger pump. The electromagnetic directional valve is used for switching an oil way of the flow distribution auxiliary testing device. The servo motor is used for driving the cylinder shaft of the flow distribution pair test device to rotate.
Furthermore, the pressure sensor is respectively used for measuring the system pressure of the high-speed high-pressure axial plunger pump flow distribution pair test bench and the pressing force of the loading piston, and the pressure sensor I is used for measuring the system pressure of the test bench, namely the actual working pressure of the plunger pump; and the second pressure sensor is used for measuring the pressing force of the loading piston, and the pressing force is used for the high-pressure plunger cavity pressing force on the cylinder in the real plunger pump. The frequency digital display meter is used for displaying dynamic measurement values of system pressure, loading piston pressing force and cylinder body main shaft rotating speed of the high-speed high-pressure axial plunger pump flow distribution pair test bench, outputting the measurement values input into the digital display meter by the two pressure sensors and the four temperature sensors to the data acquisition board card, and inputting the measurement values into the computer for storage by the data acquisition board card.
Further, the upper computer interface comprises a start-stop control area, a temperature display area, a parameter display area I, a parameter display area II and a rotating speed control area. The start-stop control area is used for controlling the start and stop of the data acquisition system, the temperature display area is used for displaying the real-time temperature of the flow distribution pair, the rotating speed control area is used for controlling the rotating speed of the servo motor, the parameter display area is used for displaying the dynamic numerical values of the parameters such as the pressure, the pressing force, the rotating speed and the torque of the system in real time, and the parameter display area is used for displaying the dynamic curves of the parameters such as the pressure, the pressing force, the rotating speed and the torque of the system in real time.
Further, a measuring system and a calculating method for friction coefficient of a plunger pump flow distribution pair are provided, wherein the calculating method comprises the following steps:
step one, after the test bed is electrified, initializing each sensor and checking whether each part is normal.
And secondly, carrying out stress analysis on the flow distribution pair test device according to a loading mode, and analyzing the types of force and moment applied to the flow distribution pair test device during working. The flow distribution pair test device is loaded by a loading piston, four oil ports are formed in the loading piston, the loading oil ports are communicated with an upper cavity of the loading piston, the hydraulic pressing force of the flow distribution pair is simulated, a leakage oil port is communicated with a lower cavity, and the pressure of a plunger pump shell is simulated. The oil inlet and the oil outlet are communicated with a kidney-shaped window of the valve plate friction plate to generate hydraulic separating force. The stress condition of the flow distribution pair under different working conditions is simulated through the interaction of the pressing force generated by the loading cylinder and the separating force generated by the waist-shaped window. A hydraulic system is built based on the principle of the test device, and the hydraulic system provides working pressure and compression pressure of a pump through an unloading overflow valve and a proportional pressure reducing valve respectively.
The stress condition of an assembly body formed by the cylinder body shaft and the cylinder body valve plate is isolated and analyzed, the stress condition comprises external force and external moment borne by the assembly body, F is the external force borne by the assembly body, and T is the external moment borne by the assembly body. Externally appliedPressing force FcThrust F to the thrust bearingBThe two forces are balanced. Drive torque T of cylinder shaftdrivenFriction torque T with flow distribution pairCVThe friction torque T borne by the cylinder shaft side wallCLfFriction torque T of thrust bearingBAnd a sealed friction torque TSfAnd balancing the sum. The friction torque acting on the flow distribution pair can be expressed as:
TCV＝Tdriven-TCLf-TBf-TSf (1.1)
drive torque T of cylinder shaftdrivenCan be measured by a torque speed sensor. Friction torque T borne by cylinder shaft side wallCLfThe viscous friction force of the oil is adopted; friction torque T of thrust bearingBfFriction torque T with sealSfIs the combined friction of coulomb friction and viscous friction. Therefore, the cylinder body axis torque can be divided into a coulomb friction part and a viscous friction part, and the situation that the torque borne by the cylinder body axis is further decomposed is shown in table 1.
TABLE 1 Friction Torque Classification
Step three, obtaining an expression of the friction coefficient of the flow distribution pair according to the stress analysis in the step two: the magnitude of the coulomb friction force is proportional to the magnitude of the normal pressure force. Coulomb friction torque T born by thrust bearingBcCan be expressed as:
sealed coulomb friction torque TScRelating to the holding force between the sealing ring and the cylinder shaft FSIt can be considered as a constant. Thus, the coulomb friction torque of the seal is expressed as:
the magnitude of the viscous friction is proportional to the speed, and the cylinder shaft is subjected to all of the viscous friction torque (T)CLv,TBvAnd TSv) The sum can be obtained by means of experiments. When externally applied pressing force FcWhen the driving torque is 0, namely when the distribution plate is completely separated from the cylinder body, the driving torque of the cylinder body shaft is the sum of the viscous friction torque and the sealed coulomb friction torque, and is expressed as follows:
Tno-load(ω)＝TSc+TCLv(ω)+TBv(ω)+TSv(ω) (1.4)
fitting the test results according to the formula (1.4) to obtain:
Tno-load(ω)＝Bint er+Kno-load·ω (1.5)
pitch B of the linear functioninterFor sealing coulomb friction torque TScMagnitude of (1), slope Kno-loadIs the rate of change of the viscous friction torque with the rotational speed. In the simultaneous relationship (1.1) to (1.5), the friction torque of the distribution pair can be expressed as:
therefore, the magnitude of the coefficient of friction of the flow distribution pair can be expressed as:
in the formula (1.7), dcvThe diameter of the reference circle of the cylinder body is in mm; a. thevFor distributing the effective action area of the side effect, unit mm2。
And step four, electrifying the test bed, pressurizing the test device and adjusting the rotating speed of the motor. Recording pressure p under different working conditions through a data acquisition systemsPressing force FcRotational speed ω, torque Tdriven. Step five, fitting the air load torque T according to the method in the step threeno-loadAnd will beAnd substituting the parameters obtained by measurement in the fourth step into the formula (1.7) in the third step to obtain the friction coefficient of the flow distribution pair.
The invention has the beneficial effects that:
1. the method can realize the measurement and calculation of the friction coefficient of the flow distribution pair of the plunger pump, deduces the friction coefficient of the flow distribution pair under the condition that the colleagues of the flow distribution pair have coulomb friction and viscous friction, and determines the friction state of the flow distribution pair;
2. the invention can realize the simulation of the pressure of the flow distribution pair of the plunger pump and realize the measurement of the pressure, the rotating speed and the pressure of the flow distribution pair;
drawings
FIG. 1 is a block diagram of a data acquisition system;
FIG. 2 is a schematic view of a hydraulic-mechanical schematic of a flow distribution pair test apparatus;
FIG. 3 is a force analysis diagram of the flow distribution pair test device;
FIG. 4 shows torque Tno-loadA linear fitting graph;
FIG. 5 is a diagram of an upper computer interface of the data acquisition system.
In the figure, 1, an accumulator; 2. a first pressure sensor; 3. a constant pressure pump station; 4. an unloading overflow valve; 5. an electromagnetic directional valve; 6. a proportional pressure reducing valve; 7. a second pressure sensor; 8. an oil inlet; 9. a first temperature sensor; 10. an oil leakage port; 11. a loading oil port; 12. an oil outlet; 13. loading the piston; 14. a cylinder shaft; 15. a servo motor; 16. a torque and rotation speed sensor; 17. a temperature display area; 18. a first parameter display area; 19. a second parameter display area; 20. a rotational speed control area; 21. a start-stop control area; 22. a first frequency digital display meter; 23. a second frequency digital display meter; 24. and a torque and rotating speed digital display meter.
Detailed Description
The invention is realized by the following technical scheme: a measuring system and a calculating method for friction coefficients of a flow distribution pair of a plunger pump are provided, wherein the system comprises a hydraulic-mechanical system for a test device of the flow distribution pair, a pressure sensor I2, a frequency digital display meter I22 corresponding to the pressure sensor, a pressure sensor II 7 and a frequency digital display meter II 23 corresponding to the pressure sensor. The torque and rotation speed sensor 16 and the corresponding torque and rotation speed digital display meter 24 comprise a temperature sensor 9, three temperature sensors 9 which are circumferentially distributed, a data acquisition board card, a computer and a self-developed upper computer data acquisition system. The number of the sensors is consistent with the number of the data input ports of the data acquisition board card, the data output of the data acquisition board card is transmitted to the computer through the USB interface, and an upper computer data acquisition system of the computer dynamically displays the data and generates a report to be stored.
Furthermore, the hydraulic-mechanical system for the flow distribution auxiliary test device comprises a constant pressure pump station 3, an energy accumulator 1, an unloading overflow valve 4, a proportional pressure reducing valve 6, an electromagnetic directional valve 5 and a servo motor 15. The constant pressure pump station 3 is used for providing constant pressure oil for the hydraulic system, the energy accumulator 1 is used for maintaining pressure of the hydraulic system, and the unloading overflow valve 4 is used for adjusting the pressure of the system and simulating the pressure of a high-pressure cavity of the plunger pump. The proportional pressure reducing valve 7 is used for adjusting the pressure of the loading piston and simulating the pressing force applied to the cylinder body of the plunger pump. The electromagnetic directional valve 5 is used for switching an oil path of the flow distribution auxiliary testing device. The servo motor 15 is used for driving the cylinder shaft 14 of the distribution auxiliary test device to rotate.
Further, the first pressure sensor 2 is used for measuring the system pressure of the test bed, namely the actual working pressure of the plunger pump; the second pressure sensor 7 is used for measuring the pressing force of the loading piston, and the pressing force is used for the high-pressure plunger cavity pressing force on the cylinder in the real plunger pump. The frequency digital display meter is used for displaying dynamic measurement values of system pressure, loading piston pressing force and cylinder body main shaft rotating speed of the high-speed high-pressure axial plunger pump flow distribution pair test bench, outputting the measurement values input into the digital display meter by the two pressure sensors and the four temperature sensors to the data acquisition board card, and inputting the measurement values into the computer for storage by the data acquisition board card.
Further, the upper computer interface comprises a start-stop control area 21, a temperature display area 17, a first parameter display area 18, a second parameter display area 19 and a rotating speed control area 20. The start-stop control area 21 is used for controlling the start and stop of the data acquisition system, the temperature display area 17 is used for displaying the real-time temperature of the flow distribution pair, the rotating speed control area 20 is used for controlling the rotating speed of the servo motor, the parameter display area I18 is used for displaying the dynamic numerical values of the parameters such as the pressure, the pressing force, the rotating speed and the torque of the system in real time, and the parameter display area II 19 is used for displaying the dynamic curves of the parameters such as the pressure, the pressing force, the rotating speed and the torque of the system in real time.
Further, a measuring system and a calculating method for friction coefficient of a plunger pump flow distribution pair are provided, wherein the calculating method comprises the following steps:
step one, after the test bed is electrified, initializing each sensor and checking whether each part is normal.
And secondly, carrying out stress analysis on the flow distribution pair test device according to a loading mode, and analyzing the types of force and moment applied to the flow distribution pair test device during working. The distribution pair testing device is loaded by a loading piston 13, four oil ports are formed in the loading piston 13, a loading oil port 11 is communicated with an upper cavity of the loading piston 13 to simulate the hydraulic pressing force of a distribution pair, and a leakage oil port 10 is communicated with a lower cavity to simulate the pressure of a plunger pump shell. The oil inlet 8 and the oil outlet 12 are communicated with a kidney-shaped window of the friction plate of the port plate to generate hydraulic separating force. The stress condition of the flow distribution pair under different working conditions is simulated through the interaction of the pressing force generated by the loading cylinder and the separating force generated by the waist-shaped window. A hydraulic system is built based on the principle of the test device, and the hydraulic system provides working pressure and compression pressure of a pump through an unloading overflow valve 14 and a proportional pressure reducing valve 6 respectively.
The stress condition of the cylinder shaft 14 is isolated and analyzed, and comprises external force and external moment borne by the assembly body, wherein F is the external force borne by the assembly body, and T is the external moment borne by the assembly body. Externally applied pressing force FcThrust F to the thrust bearingBThe two forces are balanced. Drive torque T of cylinder shaftdrivenFriction torque T with flow distribution pairCVThe friction torque T borne by the cylinder shaft side wallCLfFriction torque T of thrust bearingBAnd a sealed friction torque TSfAnd balancing the sum. The friction torque acting on the flow distribution pair can be expressed as:
TCV＝Tdriven-TCLf-TBf-TSf (2.1)
drive torque T of cylinder shaftdrivenCan be measured by the torque speed sensor 16. Friction torque T borne by cylinder shaft side wallCLfThe viscous friction force of the oil is adopted; friction torque T of thrust bearingBfFriction torque T with sealSfIs the combined friction of coulomb friction and viscous friction. Therefore, the cylinder body axis torque can be divided into a coulomb friction part and a viscous friction part, and the situation that the cylinder body axis torque is further decomposed is shown in table 2.
TABLE 2 Friction Torque Classification
Step three, obtaining an expression of the friction coefficient of the flow distribution pair according to the stress analysis in the step two: the magnitude of the coulomb friction force is proportional to the magnitude of the normal pressure force. Coulomb friction torque T born by thrust bearingBcCan be expressed as:
sealed coulomb friction torque TScRelating to the holding force between the sealing ring and the cylinder shaft FSIt can be considered as a constant. Thus, the coulomb friction torque of the seal is expressed as:
the magnitude of the viscous friction is proportional to the speed, and the cylinder shaft is subjected to all of the viscous friction torque (T)CLv,TBvAnd TSv) The sum can be obtained by means of experiments. When the external pressing force is 0, namely the distribution plate is completely separated from the cylinder body, the driving torque of the cylinder body shaft is the sum of the viscous friction torque and the sealed coulomb friction torque, and is expressed as follows:
Tno-load(ω)＝TSc+TCLv(ω)+TBv(ω)+TSv(ω) (2.4)
fitting the test results according to formula (4) to obtain:
Tno-load(ω)＝Binter+Kno-load·ω (2.5)
pitch B of the linear functioninterFor sealing coulomb friction torque TScMagnitude of (1), slope Kno-loadIs the rate of change of the viscous friction torque with the rotational speed. In the simultaneous relationship (2.1) to (2.5), the friction torque of the distribution pair can be expressed as:
therefore, the magnitude of the coefficient of friction of the flow distribution pair can be expressed as:
in the formula (2.7), dcvThe diameter of the reference circle of the cylinder body is in mm; a. thevFor distributing the effective action area of the side effect, unit mm2。
And step four, electrifying the test bed, pressurizing the test device and adjusting the rotating speed of the servo motor 15. Recording pressure p under different working conditions through a data acquisition systemsPressing force FcRotational speed ω, torque Tdriven. Step five, fitting the air load torque T according to the method in the step threeno-loadAnd substituting the parameters obtained by measurement in the fourth step into the formula (2.7) in the third step to obtain the friction coefficient of the flow distribution pair.
It will be appreciated by those skilled in the art that changes, modifications, substitutions and alterations can be made in the embodiments described above without departing from the principles and spirit of the invention, the scope of which is defined by the appended claims.
Claims (5)
1. A measuring system and a calculating method for friction coefficient of a plunger pump flow distribution pair are disclosed, the measuring system comprises a hydraulic-mechanical system for a flow distribution pair test device, two pressure sensors and frequency digital display tables corresponding to the pressure sensors, a torque rotating speed sensor and a torque rotating speed digital display table corresponding to the torque rotating speed sensor, four temperature sensors, a sublimation data acquisition board card, a computer and a self-developed upper computer data acquisition system, and is characterized in that: the number of the sensors is consistent with the number of the data input ports of the data acquisition board card, the data output of the porphyry data acquisition board card is transmitted to the computer through the USB interface, and an upper computer data acquisition system of the computer dynamically displays the data and generates a report for storage.
2. The measurement system applied to the high-speed high-pressure axial plunger pump flow distribution pair test device as claimed in claim 1, wherein: the hydraulic-mechanical system comprises a constant pressure pump station, an energy accumulator, an unloading overflow valve, a proportional pressure reducing valve, an electromagnetic directional valve and a servo motor, wherein the constant pressure pump station is used for providing constant pressure oil for the hydraulic system, the energy accumulator is used for maintaining pressure of the hydraulic system, the unloading overflow valve is used for adjusting the pressure of the system and simulating the pressure of a high-pressure cavity of the plunger pump, the pressure reducing valve is used for adjusting the pressure of a loading piston and simulating the pressing force applied to a cylinder body of the plunger pump, and the magnetic directional valve is used for switching an oil way of the flow distribution pair testing device. The servo motor is used for driving the cylinder shaft of the flow distribution pair test device to rotate.
3. The measurement system applied to the high-speed high-pressure axial plunger pump flow distribution pair test device as claimed in claim 1, wherein: the pressure sensor is respectively used for measuring the system pressure and the loading piston pressing force of the high-speed high-pressure axial plunger pump flow distribution pair test bench, and the pressure sensor I is used for measuring the system pressure of the test bench, namely the actual working pressure of the plunger pump; and the frequency digital display meter is used for displaying dynamic measurement values of the system pressure of the high-speed high-pressure axial plunger pump flow distribution pair test bench, the pressing force of the loading piston and the rotating speed of the main shaft of the cylinder body, outputting the measurement values input into the digital display meter by the two pressure sensors and the four temperature sensors to the data acquisition board card, and inputting the measurement values into the computer for storage by the data acquisition board card.
4. The measurement system applied to the high-speed high-pressure axial plunger pump flow distribution pair test device as claimed in claim 1, wherein: the upper computer data acquisition system interface comprises a start-stop control area, a temperature display area, a parameter display area I, a parameter display area II and a rotating speed control area, wherein the start-stop control area is used for controlling the start and stop of the data acquisition system, the temperature display area is used for displaying the real-time temperature of the flow distribution pair, the rotating speed control area is used for controlling the rotating speed of the servo motor, the parameter display area I is used for displaying the dynamic numerical values of the parameters such as the pressure, the pressing force, the rotating speed and the torque of the system in real time, and the parameter display area II is used for displaying the dynamic curves of the parameters such as the pressure, the pressing force, the rotating speed and the torque of the system in real time.
5. A measuring system and a calculating method for friction coefficient of a flow distribution pair of a plunger pump are characterized in that: the calculation method is as follows,
step one, after the test bed is electrified, initializing each sensor and checking whether each part is normal;
step two, according to the loading mode, carry out the atress analysis to the vice test device that flows, the kind of the power and the moment that the vice test device that flows that analysis flow received at the during operation, its characterized in that: the distribution pair test device is loaded by a loading piston, four oil ports are formed in the loading piston, the loading oil ports are communicated with an upper cavity of the loading piston, the hydraulic pressing force of a distribution pair is simulated, a leakage oil port is communicated with a lower cavity, the pressure of a shell of a plunger pump is simulated, an oil inlet and an oil outlet are communicated with a kidney-shaped window of a friction plate of a distribution plate to generate hydraulic separation force, the interaction of the pressing force generated by a loading cylinder and the separation force generated by the kidney-shaped window is used for simulating the stress condition of the distribution pair under different working conditions, and a hydraulic system respectively provides the working pressure and the pressing pressure of a pump through an unloading valve and a proportional pressure reducing valve;
the stress condition of an assembly body formed by the cylinder body shaft and the cylinder body valve plate is isolated and analyzed, and the stress condition comprises external force and external moment borne by the assembly body, wherein F is the external force borne by the assembly body, T is the external moment borne by the assembly body, and external applied pressing force FcThrust F to the thrust bearingBTwo-force balance, drive torque T of cylinder shaftdrivenFriction torque T with flow distribution pairCVThe friction torque T borne by the cylinder shaft side wallCLfFriction torque T of thrust bearingBAnd a sealed friction torque TSfIn sum balance, the friction torque acting on the flow distribution pair can be expressed as:
TCV＝Tdriven-TCLf-TBf-TSf (1)
drive torque T of cylinder shaftdrivenCan be measured by a torque and rotation speed sensor, and the friction torque T born by the side wall of the cylinder body shaftCLfThe viscous friction force of the oil is adopted; friction torque T of thrust bearingBfFriction torque T with sealSfThe friction torque T of the thrust bearing is combined by the Coulomb friction and the viscous frictionBfFriction torque T with sealSfDividing the cylinder body into a coulomb friction part and a viscous friction part, respectively solving, and further decomposing the torque borne by the cylinder body shaft as shown in table 1;
TABLE 1 Friction Torque Classification
Step three, obtaining an expression of the friction coefficient of the flow distribution pair according to the stress analysis in the step two: the magnitude of the coulomb friction force is proportional to the magnitude of the normal pressure force. Coulomb friction torque T born by thrust bearingBcCan be expressed as:
sealed coulomb friction torque TScRelating to the holding force between the sealing ring and the cylinder shaft FSIt can be considered as a constant. Thus, the coulomb friction torque of the seal is expressed as:
the magnitude of the viscous friction is proportional to the speed, and the cylinder shaft is subjected to all of the viscous friction torque (T)CLv,TBvAnd TSv) The sum can be obtained by means of tests, said externally applied pressing force FcWhen the driving torque is 0, namely when the distribution plate is completely separated from the cylinder body, the driving torque of the cylinder body shaft is the sum of the viscous friction torque and the sealed coulomb friction torque, and is expressed as follows:
Tno-load(ω)＝TSc+TCLv(ω)+TBv(ω)+TSv(ω) (4)
fitting the test results according to formula (4) to obtain:
Tno-load(ω)＝Binter+Kno-load·ω (5)
pitch B of the linear functioninterFor sealing coulomb friction torque TScMagnitude of (1), slope Kno-loadIs the rate of change of the viscous friction torque with the rotational speed. Simultaneous (3.1) - (3.5), the friction moment of the distribution pair can be expressed as:
therefore, the magnitude of the friction coefficient of the flow pair can be expressed as:
in the formula (7), dcvThe diameter of the reference circle of the cylinder body is in mm; a. thevFor distributing the effective action area of the side effect, unit mm2，
Step four, electrifying the test bed, pressurizing the test device, adjusting the rotating speed of the motor, and recording the pressure p under different working conditions through the data acquisition systemsPressing force FcRotational speed ω, torque TdrivenStep five, fitting the air load torque T according to the method in the step threeno-loadSubstituting the parameters obtained by measurement in the fourth step into the formula (7) in the third step to obtain the friction coefficient of the flow distribution pair.
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114623128A (en) * | 2022-03-31 | 2022-06-14 | 中南大学 | Hydraulic system for testing oil film characteristic of flow distribution pair of axial plunger pump |
| CN114623128B (en) * | 2022-03-31 | 2022-12-23 | 中南大学 | Hydraulic system for testing oil film characteristics of flow distribution pair of axial plunger pump |
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