CN115076086B - Fault simulation method and test device for plunger pump under multiple working conditions - Google Patents
Fault simulation method and test device for plunger pump under multiple working conditions Download PDFInfo
- Publication number
- CN115076086B CN115076086B CN202210689129.2A CN202210689129A CN115076086B CN 115076086 B CN115076086 B CN 115076086B CN 202210689129 A CN202210689129 A CN 202210689129A CN 115076086 B CN115076086 B CN 115076086B
- Authority
- CN
- China
- Prior art keywords
- plunger pump
- fault
- oil
- data
- valve
- 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.)
- Active
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B51/00—Testing machines, pumps, or pumping installations
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Abstract
The invention provides a fault simulation method and a test device for a plunger pump under multiple working conditions, which comprises the following specific processes: the automatic reversing of the hydraulic cylinder is realized by adjusting various operating parameters, replacing parts with different damage degrees in the plunger pump and utilizing the electromagnetic reversing valve and the two inductive proximity switches, so that single fault simulation that the abrasion loss, the damage degree and the shoe loosening degree of different elements of the plunger pump are gradually deepened under multiple working conditions of variable load, variable temperature and variable flow is realized; carrying out combined composite fault simulation on the single fault and hydraulic impact simulation on a hydraulic system under multiple working conditions; and finally, acquiring and storing fault data in different modes. The invention perfects the plunger pump fault database, facilitates the technical personnel to identify the fault type and degree, simultaneously realizes low acquisition cost and high fault coverage by the optimized design of schemes of replacing plunger pump vulnerable parts, deepening the fault degree step by step and the like, and provides a new method for the fault diagnosis simulation of the plunger pump.
Description
Technical Field
The invention relates to the technical field of plunger pump fault simulation, in particular to a fault simulation method and a multi-fault simulation test device for a plunger pump under multiple working conditions.
Background
The plunger pump is used as a main power element of a hydraulic system, has the advantages of high rated pressure, high power, high efficiency, small volume and the like, and is widely applied to occasions with high pressure, large flow and flow needing to be adjusted, such as hydraulic machines, engineering machinery and ships. But also has the defects of poor self-absorption, complex structure, high oil precision requirement, high maintenance cost and the like. The common faults of the swash plate type axial plunger pump include three friction pairs and abrasion: the wear of a slipper pair formed by the slipper and a swash plate, the wear of a plunger pair formed by a plunger and a cylinder body, the wear of a flow distribution pair formed by the cylinder body and a flow distribution plate, the fault of loose shoes, the fault of a bearing of a plunger pump and the like.
The working environment of the plunger pump is relatively severe, and the plunger pump is in a working state of high pressure and high speed operation for a long time, so that various faults can not be avoided, and once the plunger pump has the characteristics of diversity and uncertainty, the normal operation of equipment can be influenced, serious economic loss can be caused, and personal safety can be caused under certain conditions. Therefore, how to quickly find out the fault and even find out the symptom of the fault in advance is an urgent problem to be solved, so that the method is particularly important for performing fault simulation test work on the plunger pump, perfecting a fault database and ensuring that the plunger pump runs safely and stably. At present, fault diagnosis of the plunger pump mainly judges whether the plunger pump works normally or not through various monitoring means, and a large amount of time and financial resources are consumed, so that complete fault data are provided for discovering fault signs in advance in order to better research the running states of the plunger pump under different wear degrees, and therefore, the economic test device and the method capable of simulating multiple fault modes are very important.
Disclosure of Invention
Aiming at the problems in the prior art, the invention provides a fault simulation method and a test device thereof for a plunger pump under multiple working conditions, which realize fault simulation of gradually deepening the abrasion loss, the damage degree and the shoe loosening degree of each element of the plunger pump under multiple working conditions of variable load, variable temperature and variable flow by adjusting multiple operating parameters, replacing parts with different damage degrees in the plunger pump and changing the direction of a piston of a hydraulic cylinder, thereby providing fault data more fitting the actual working conditions, perfecting an incomplete plunger pump fault database and providing more powerful reference for fault diagnosis of the plunger pump.
The invention provides a fault simulation method for a plunger pump under multiple working conditions, which specifically comprises the following steps:
s1, collecting test data of a plunger pump in a normal state, and establishing test data type expressions in the normal state and a fault state, wherein the specific expressions are as follows:
wherein K is the type of experimental data; x is the number of T Is a temperature state type; x is a radical of a fluorine atom p Is a pressure state type; x is the number of q Is a traffic status category; x is the number of s Is a sampling frequency category; x is the number of e Is a fault category; x is the number of g To the extent of failureThe number of the particles; n is the fault category taken for the composite fault, (n =1,2, 3);
s2, collecting test data of the plunger pump in a multi-working-condition fault state:
s21, simulating single failure or composite failure of the plunger pump through optimized design, considering the abrasion loss, the damage degree and the shoe loosening degree of different internal elements according to the failure type of the plunger pump, and setting failure grades of different degrees;
s22, starting a plunger pump driving motor, and running in the fault plunger pump according to the oil temperature and the fault type;
s23, after the fault plunger pump operates stably in the hydraulic system, the two-position two-way electromagnetic directional valve is electrified, and the three-position four-way electromagnetic directional valve is in a neutral position when the three-position four-way electromagnetic directional valve is electrified;
s24, respectively setting the pressure of a proportional overflow valve and the flow of a proportional throttle valve according to the setting of the pressure, the flow and the temperature of the hydraulic system in the step S1, and setting different temperatures by matching the preset running time of the plunger pump with a fan cooler so that the plunger pumps with different fault levels respectively run once in multiple states of the three conditions of the pressure, the flow and the temperature;
s25, calculating the volumetric efficiency eta of the plunger pump with different faults in different fault types according to the data collected in the step S24 v Said volumetric efficiency η v The calculation expression of (a) is as follows:
η v ＝(q 1 +q 2 )/(q 1 +q 2 +Δq)
where Δ q is the leakage flow rate of the plunger pump collected by the first flow meter in each failure simulation, q 1 For the flow of the main circuit, q, taken by the second flow meter in the respective time during each fault simulation 2 The overflow flow of the overflow loop collected by the third flow meter in corresponding time in each fault simulation;
s26, after each fault state data acquisition is completed, the two-position two-way electromagnetic directional valve is powered off, and the electromagnet at the left end of the three-position four-way electromagnetic directional valve is powered on, so that the system is connected with a hydraulic impact oil way;
s27, repeating the numerical setting of temperature, pressure, flow and sampling frequency in the step S1, acquiring acceleration sensor data of a plunger pump shell along X, Y and Z directions and data of a flow meter, a pressure sensor, a temperature sensor and a sound level meter in the fault state of the plunger pump when the hydraulic pressure impacts an oil way each time on the premise of certain sampling time, sampling times and sampling intervals, and recording the reversing times of the piston;
and S3, taking the data collected in S1 and S2 as original data and storing the original data.
Preferably, the specific implementation process of step S1 is:
s11, starting a plunger pump hydraulic system, and enabling a two-position two-way electromagnetic directional valve to be electrified and a three-position four-way electromagnetic directional valve to be in a neutral position after the plunger pump runs stably in the system, so that the plunger pump hydraulic system is in a variable-load oil way;
s12, setting test parameters such as temperature, pressure, flow, sampling frequency and the like of test working conditions, and acquiring acceleration sensor data of a plunger pump shell in X, Y and Z directions and data of a flowmeter, a pressure sensor, a temperature sensor and a sound level meter in the normal state of the plunger pump in a variable load oil way each time on the premise of certain sampling time, sampling times and sampling intervals;
s13, the two-position two-way electromagnetic reversing valve is powered off, electromagnets at two ends of the three-position four-way electromagnetic reversing valve are alternately powered on, and the plunger pump hydraulic system is located in a hydraulic impact oil way;
s14, fixing the relative positions of two inductive proximity switches positioned at the rod end of the hydraulic cylinder, acquiring acceleration sensor data of a plunger pump shell in the X direction, the Y direction and the Z direction and data of a flow meter, a pressure sensor, a temperature sensor and a sound level meter under the normal state of the plunger pump in a hydraulic impact oil way on the premise of certain sampling times, sampling intervals and sampling time, and recording the piston reversing times.
Preferably, in step S14, the data is acquired by each sensor when the hydraulic cylinder piston is operating normally and at the moment of switching the direction.
Preferably, in step S21, the failure type of the plunger pump includes wear amounts of the respective elements such as the sliding shoes, the plunger, and the port plate, a degree of shoe loosening of the sliding shoes, and a degree of damage to the inner ring, the outer ring, and the rolling elements of the rolling bearing.
Preferably, the specific implementation process of step S24 is:
s241, under the same sampling time, sampling times and sampling interval as those in the step S12, acquiring the sampling frequency d 1 Data of a sound level meter, a flow meter, a pressure sensor, a temperature sensor and an acceleration sensor in a kHz state;
s242, repeating the step S241, and collecting the sampling frequency d 2 In the kHz state, data of a sound level meter, a flow meter, a pressure sensor, a temperature sensor and an acceleration sensor.
In another aspect of the invention, a multi-fault simulation test device for a fault simulation method of a plunger pump under multiple working conditions is provided, which comprises an oil tank, an oil absorption filter, a flow meter, a thermometer, an air cleaner, a liquid level meter, a plunger pump driving motor, a high-pressure filter, a check valve, a pressure sensor, a quick-change connector, a proportional overflow valve, a pressure meter, a temperature sensor, an oil return filter and a fan cooler, wherein an oil suction port of the plunger pump is connected with a first end of the oil tank through the oil absorption filter, an output end of the plunger pump driving motor is connected with the first end of the plunger pump, an oil drainage end of the plunger pump is connected with a second end of the oil tank through the first flow meter, the proportional overflow valve and a third flow meter, a first oil outlet end of the plunger pump is connected with a third end of the oil tank through the high-pressure filter, the proportional overflow valve and the third flow meter in sequence, an oil inlet end of the plunger pump and the temperature sensor are connected with an oil inlet of a proportional throttle valve and a three-position electromagnetic reversing valve in a simulation hydraulic shock oil path in parallel connection, and a four-way electromagnetic impact oil tank and a filter are connected with a four-way filter. The analog variable load oil way comprises a proportional throttle valve and a two-position two-way electromagnetic reversing valve, wherein an oil outlet of the proportional throttle valve is connected with an oil inlet of the two-position two-way electromagnetic reversing valve; the simulation hydraulic impact oil way comprises a three-position four-way electromagnetic reversing valve, a first one-way throttle valve, a hydraulic cylinder and a second one-way throttle valve, wherein a first oil outlet of the three-position four-way electromagnetic reversing valve is connected with an oil inlet of the first one-way throttle valve, an oil outlet of the first one-way throttle valve is connected with a rodless end of the hydraulic cylinder, a rod end of the hydraulic cylinder is connected with an oil inlet of the second one-way throttle valve, an oil outlet of the second one-way throttle valve is connected with a second oil outlet of the three-position four-way electromagnetic reversing valve, a third oil outlet of the three-position four-way electromagnetic reversing valve is connected with an oil outlet of the two-position two-way electromagnetic reversing valve in parallel, and the three-position four-way electromagnetic reversing valve is connected with a seventh end of an oil tank sequentially through an oil return filter and a fan cooler.
Compared with the prior art, the invention has the following advantages:
1. the invention realizes single fault simulation of gradual deepening of abrasion loss, damage degree and shoe loosening degree of various elements such as piston pump sliding shoes, plungers, valve plates, bearing inner rings, outer rings, rolling bodies and the like under the multi-working conditions of variable load, variable temperature and variable flow by adjusting various operating parameters, replacing parts with different damage degrees in the pump and changing the direction of the piston of the hydraulic cylinder, and is convenient for technical personnel to find fault phenomena and identify fault types and degrees.
2. The invention combines single fault to realize composite fault simulation and hydraulic impact simulation of a hydraulic system under multiple working conditions, and simultaneously collects system pressure, flow, temperature, sound and vibration acceleration data of the plunger pump under different modes, thereby providing fault data more fitting actual working conditions, perfecting an incomplete plunger pump fault database, and providing more powerful reference for fault diagnosis of the plunger pump.
Drawings
FIG. 1 is a flow chart of a fault simulation method for a plunger pump under multiple operating conditions according to the present invention;
FIG. 2 is a hydraulic schematic diagram of a multi-fault simulation test device for the fault simulation method of the plunger pump under multiple working conditions.
The main reference numbers:
the device comprises an oil tank 1, an oil absorption filter 2, a first flowmeter 3, a thermometer 4, an air filter 5, a liquid level meter 6, a plunger pump 7, a plunger pump driving motor 8, a second flowmeter 9, a third flowmeter 10, a high-pressure filter 11, a one-way valve 12, a pressure sensor 13, a quick-change connector 14, a proportional overflow valve 15, a pressure gauge 16, a temperature sensor 17, a proportional throttle valve 18, a two-position two-way electromagnetic reversing valve 19, an oil return filter 20, a fan cooler 21, a three-position four-way electromagnetic reversing valve 22, a first one-way throttle valve 23, a hydraulic cylinder 24 and a second one-way throttle valve 25.
Detailed Description
The technical contents, structural features, attained objects and effects of the present invention are explained in detail below with reference to the accompanying drawings.
The method for simulating the faults of the plunger pump under the multiple working conditions comprises the steps of simulating multiple fault type tests of the plunger pump 7 under the multiple working conditions of variable load, variable temperature and variable flow by adjusting multiple operation parameters, replacing components with different damage degrees in the plunger pump 7 and changing the reversing of a hydraulic cylinder 24, and realizing the hydraulic impact of a hydraulic system with the hydraulic cylinder 24 automatically reversing under the control of a three-position four-way electromagnetic reversing valve 22 by using two inductive proximity switches, and meanwhile, collecting vibration and sound data of the plunger pump 7 and pressure, flow and temperature data of the system under different modes by using an acceleration sensor arranged on the plunger pump 7, a first flowmeter 3, a second flowmeter 9, a third flowmeter 10, a pressure sensor 13, a temperature sensor 17 and an external sound level meter which are connected to the hydraulic system and matching with a LabVIEW data collecting system, and calculating the volumetric efficiency by using the flowmeters to check the influence of the wear degree on the performance of the plunger pump. The data collected during hydraulic impact simulation are mainly used for analyzing the fluctuation influence on pressure, flow, sound and vibration acceleration signals during impact, and obtaining the influence degree of the impact times on the service life and the performance of the pump. As shown in fig. 1, the following two processes are involved:
s1, collecting test data of the plunger pump 7 in a normal state.
S2, collecting test data of the plunger pump 7 in a multi-working-condition fault state.
Specifically, the various operating parameters are pressure, flow and temperature, wherein the pressure and the flow are respectively regulated by controlling the proportional relief valve 15 and the proportional throttle valve 18 through LabVIEW software programming, and the temperature is regulated by matching the plunger pump with the fan cooler 21 in running for a certain time.
The fault simulation method for the plunger pump under multiple working conditions comprises the following specific implementation steps:
s1, collecting test data of the plunger pump 7 in a normal state, wherein a specific expression of the type of the test data is as follows:
wherein K is the type of experimental data; x is the number of T Is a temperature state type; x is the number of p Is a pressure state type; x is the number of q Is a traffic status category; x is the number of s Is a sampling frequency category; x is the number of e Is a fault category; x is the number of g The number of fault degrees; n is the fault category taken for the composite fault, (n =1,2, 3).
S11, starting a plunger pump hydraulic system, and enabling the two-position two-way electromagnetic directional valve 19 to be electrified and the three-position four-way electromagnetic directional valve 22 to be in a middle position after the plunger pump 7 runs stably in the system, so that the plunger pump hydraulic system is in a variable-load oil way.
S12, designing a test working condition, and setting the temperature as a through the matching of the plunger pump running-in preset time and the fan cooler 21 1 ～a 2 ℃、a 3 ～a 4 DEG C and a 5 ～a 6 Setting the pressure of proportional relief valve 15 at b deg.C 1 MPa、b 2 MPa and b 3 Three conditions of MPa, the flow of the proportional throttle valve 18 is set as c 1 L/min、c 2 L/min and c 3 The three states of L/min enable the system to cover more working conditions close to the actual working conditions; designing test parameters, and setting the sampling frequency as d 1 kHz and d 2 kHz two frequencies are used for providing data with different frequencies for later data use; on the premise of certain sampling time, sampling times and sampling intervals, acceleration sensor data of the plunger pump shell in the X direction, the Y direction and the Z direction and data of a flowmeter, a pressure sensor 13, a temperature sensor 17 and a sound level meter in the normal state of the plunger pump 7 in the variable-load oil way are collected, and a large amount of data support is provided for multi-sensor data fusion fault diagnosis.
And S13, the two-position two-way electromagnetic directional valve 19 is powered off, and electromagnets at two ends of the three-position four-way electromagnetic directional valve 22 are alternately powered on, so that the plunger pump hydraulic system is positioned in a hydraulic impact oil way.
And S14, repeating the numerical setting of the temperature, the pressure, the flow and the sampling frequency in the step S12, and acquiring the data of acceleration sensors of the plunger pump shell in the X direction, the Y direction and the Z direction and the data of a flowmeter, a pressure sensor 13, a temperature sensor 17 and a sound level meter under the condition that the plunger pump 7 in a hydraulic impact oil path is in a normal state under the premise that the relative positions of two inductive proximity switches fixedly positioned at the rod ends of the hydraulic cylinder 24 and provided with a certain sampling frequency, sampling interval and sampling time each time, and recording the piston reversing frequency.
Preferably, in step S14, the data is acquired by each sensor when the piston of the hydraulic cylinder 24 is normally operated and at the moment of switching the direction.
S2, collecting test data of the plunger pump 7 in a multi-working-condition fault state.
S21, simulating single fault or composite fault of the plunger pump 7 according to the optimized design, and setting fault grades of different degrees according to the fault type of the plunger pump 7, the abrasion loss of different internal elements, the damage degree and the shoe loosening degree.
Specifically, in order to provide a more complete criterion of fault type and fault degree of the plunger pump 7, single fault and composite fault simulation is performed on the plunger pump 7, from the perspective of reducing test cost and avoiding replacement of the whole plunger pump 7, multiple sets of accessories are purchased and replaced through optimized design, faults of internal parts of the plunger pump 7 are simulated, faults under multiple working conditions are simulated through changes of operating parameters such as pressure, flow and temperature in the test process, vibration acceleration and sound signals are collected, leakage is calculated to serve as characteristic original data for further fault diagnosis and service life prediction, the artificial abrasion loss is estimated according to the model and working condition range of the tested plunger pump 7 and the volume efficiency of the plunger pump, therefore, different fault levels are set, the contradiction requirements on the quantity requirements of the fault levels and the saving of the test cost are analyzed for balanced modeling, most of single faults are set to three fault levels, and different composite faults and levels are formed according to the combination of two to three single faults.
Further, the failure type of the plunger pump 7 is simulated according to a failure mode which is common in actual production operation, so that the failure type has typicality and consists of abrasion of a sliding shoe, a plunger, a port plate and a rolling bearing. The purchase and the change of many sets of accessories refer to taking into account that experimental cost is minimum, only purchases and changes the corresponding accessory of simulation trouble, if: the piston comprises a sliding shoe, a plunger, a valve plate and a rolling bearing.
The various failure type tests of the plunger pump 7 include: the single fault simulation that the abrasion loss, the damage degree and the shoe loosening degree of various elements such as piston pump sliding shoes, a piston, a valve plate, a bearing inner ring, a bearing outer ring and a rolling body are deepened step by step; and the single faults are combined to realize composite fault simulation.
And S22, starting the plunger pump driving motor 8, and running in the fault plunger pump according to the oil temperature and the fault type.
Specifically, oil films are established between a plurality of kinematic pairs of the plunger pump 7 after running and running, for example, oil films are established between a plunger and a cylinder block, a slipper and a swash plate and the like; meanwhile, the running-in can also clean the pollution of impurities such as metal powder and the like generated when the plunger pump 7 is assembled, disassembled and replaced and a fault part is arranged.
And S23, when the fault plunger pump stably runs in the hydraulic system, the two-position two-way electromagnetic directional valve 19 is electrified, and the three-position four-way electromagnetic directional valve 22 is in a neutral position when being electrified.
And S24, respectively setting the pressure of the proportional relief valve 15 and the flow of the proportional throttle valve 18 according to the setting of the pressure, the flow and the temperature of the hydraulic system in the step S1, and setting different temperatures by matching the preset running time of the plunger pump with the fan cooler 21 so as to enable the plunger pump 7 with different fault levels to respectively run once under various states of the three conditions of the pressure, the flow and the temperature.
S25, calculating the volumetric efficiency eta of the plunger pump 7 with faults of different degrees in different fault types according to the data collected in the step S24 v Volumetric efficiency η v The calculation expression of (a) is as follows:
η v ＝(q 1 +q 2 )/(q 1 +q 2 +Δq)
where Δ q is the leak flow rate of the plunger pump 7 collected by the first flow meter 3 in each failure simulation, q 1 For the flow of the main circuit, q, which is detected by the second flow meter 9 at the respective time during each fault simulation 2 And providing a quantitative criterion for the health condition of the plunger pump by calculating the volumetric efficiency for the overflow flow of the overflow circuit collected by the third flow meter 10 in corresponding time in each fault simulation.
Specifically, the main loop comprises an oil tank 1, an oil suction filter 2, a plunger pump 7, a second flow meter 9, a one-way valve 12, a pressure sensor 13, an oil return filter 20, a fan cooler 21, a quick-change connector 14 and a pressure gauge 16; and the overflow loop comprises an oil tank 1, an oil suction filter 2, a plunger pump 7, a third flow meter 10, a high-pressure filter 11 and a proportional overflow valve 15.
The specific expression of the leakage flow rate and the shoe clearance of the plunger pump is as follows:
wherein R is the outer radius of the seal band, R is the radius of the seal band in width, p is the pressure at the radius R, mu is the dynamic viscosity of the oil, and h is the annular gap formed between the seal band and the swash plate surface.
From the above formula, the leakage flow rate is proportional to the cube of the shoe clearance, and the clearance between the friction pairs has a large influence on the leakage amount, so that the degree of wear of the plunger pump can be reflected by observing the leakage amount.
And S26, after each fault state data acquisition is finished, the two-position two-way electromagnetic directional valve 19 is powered off, and the electromagnet at the left end of the three-position four-way electromagnetic directional valve 22 is powered on, so that the system is connected with a hydraulic impact oil way.
And S27, repeating the numerical setting of the temperature, the pressure, the flow and the sampling frequency in the step S1, acquiring acceleration sensor data of a plunger pump shell along the X direction, the Y direction and the Z direction and data of a flowmeter, a pressure sensor 13, a temperature sensor 17 and a sound level meter under the fault state of the plunger pump in the hydraulic impact oil way each time on the premise of certain sampling time, sampling times and sampling intervals, and recording the reversing times of the piston.
Specifically, the main working principle of the hydraulic impact working condition is as follows: the automatic switching of the extension and the retraction of a piston in a hydraulic cylinder 24 is realized by two inductive proximity switches under the control of a three-position four-way electromagnetic directional valve 22. When the two-position two-way electromagnetic directional valve 19 is powered off, the electromagnet at the left end of the three-position four-way electromagnetic directional valve 22 is powered on, the piston of the hydraulic cylinder 24 is in an extending state, when the piston head of the hydraulic cylinder 24 is sensed by the inductive proximity switch, the electromagnet at the right end of the three-position four-way electromagnetic directional valve 22 is powered on, the directional valve is in a right position, the piston of the hydraulic cylinder 24 is in a contracting state, and hydraulic impact is completed at the moment when the piston of the hydraulic cylinder 24 is switched between extending and contracting. Wherein. The hydraulic impact frequency is realized by controlling the reversing frequency of a hydraulic cylinder 24 by the relative distance between a three-position four-way electromagnetic reversing valve 22 and two inductive proximity switches, and the hydraulic impact amplitude is controlled by the overflow pressure of a proportional overflow valve 15.
And S3, taking the data collected in S1 and S2 as original data and storing the original data.
Specifically, for the stored collected multi-sensor data, aiming at different research methods and ideas, data processing methods such as signal noise reduction, feature extraction and feature dimension reduction are adopted to carry out preliminary analysis on the original data, or normal state data is compared, and methods such as machine learning and neural network are further adopted to realize the research on the contents of fault diagnosis, fault prediction and health management, service life prediction, operation reliability evaluation and the like of the axial plunger pump.
Further, the specific process of measuring the data of the plunger pump 7 under the three conditions of pressure, flow rate and temperature in step S24 includes:
s241, under the same sampling time, sampling times and sampling interval as those in the step S12, acquiring the sampling frequency d 1 In the kHz state, data of a sound level meter, a flow meter, a pressure sensor 13, a temperature sensor 17, and an acceleration sensor.
S242, repeating the step S241, and collecting the sampling frequency d 2 In the kHz state, data of a sound level meter, a flow meter, a pressure sensor 13, a temperature sensor 17, and an acceleration sensor.
As shown in fig. 2, the multi-fault simulation test device for the data acquisition method of the plunger pump under multiple operating conditions comprises an oil tank 1, an oil suction filter 2, a first flowmeter 3, a second flowmeter 9, a third flowmeter 10, a thermometer 4, an air cleaner 5, a liquid level meter 6, a plunger pump 7, a plunger pump driving motor 8, a high-pressure filter 11, a check valve 12, a pressure sensor 13, a quick-change connector 14, a proportional overflow valve 15, a pressure gauge 16, a temperature sensor 17, an oil return filter 20 and a fan cooler 21.
The first flowmeter 3, the second flowmeter 9, the third flowmeter 10, the temperature sensor 17 and the pressure sensor 13 are respectively connected with a signal input end of the A/V conversion module through wiring harnesses, a signal output end of the A/V conversion module is connected with the data acquisition module through the wiring harnesses and is communicated with a data acquisition controller embedded in a case, and the case is connected with a display.
An oil suction port of a plunger pump 7 is connected with a first end of an oil tank 1 through an oil suction filter 2, an output end of a plunger pump driving motor 8 is connected with the first end of the plunger pump 7, an oil drainage end of the plunger pump 7 is connected with a second end of the oil tank 1 through a first flowmeter 3, a first oil outlet end of the plunger pump 7 is connected with a third end of the oil tank 1 through a high-pressure filter 11, a proportional overflow valve 15 and a third flowmeter 10 in sequence, a second oil outlet end of the plunger pump 7 is connected with an oil inlet of a proportional throttle valve 18 in an analog variable load oil path and an oil inlet of a three-position four-way electromagnetic reversing valve 22 in an analog hydraulic impact oil path in parallel through a second flowmeter 9, a one-way valve 12, a pressure sensor 13 and an oil inlet and a temperature sensor 17 of a quick-change joint 14 in sequence, an oil outlet of the quick-change joint 14 is connected with a pressure gauge 16, and a fourth end, a fifth end and a sixth end of the oil tank 1 are connected with a liquid level gauge 6, an air cleaner 5 and a thermometer 4 respectively. The top and the edge of the oil tank 1 are provided with platforms for mounting hydraulic elements, and the bottom of the oil tank 1 is provided with a fixable movable caster.
The simulation variable load oil circuit comprises a proportional throttle valve 18 and a two-position two-way electromagnetic directional valve 19, the variable load working condition is simulated by adjusting the opening degree of the proportional throttle valve 18, and the oil outlet of the proportional throttle valve 18 is connected with the oil inlet of the two-position two-way electromagnetic directional valve 19. The simulation hydraulic shock oil circuit comprises a three-position four-way electromagnetic reversing valve 22, a first one-way throttle valve 23, a hydraulic cylinder 24 and a second one-way throttle valve 25, wherein a first oil outlet of the three-position four-way electromagnetic reversing valve 22 is connected with an oil inlet of the first one-way throttle valve 23, an oil outlet of the first one-way throttle valve 23 is connected with a rodless end of the hydraulic cylinder 24, a rod end of the hydraulic cylinder 24 is connected with an oil inlet of the second one-way throttle valve 25, an oil outlet of the second one-way throttle valve 25 is connected with a second oil outlet of the three-position four-way electromagnetic reversing valve 22, hydraulic shock is simulated through reversing of the hydraulic cylinder 24, a third oil outlet of the three-position four-way electromagnetic reversing valve 22 is connected with an oil outlet of the two-position two-way electromagnetic reversing valve 19 in parallel, and the oil circuit is connected with a seventh end of an oil tank 1 sequentially through an oil return filter 20 and a fan cooler 21.
Specifically, the hydraulic cylinder 24 is arranged on a rack on the side surface of the oil tank 1, and two inductive proximity switches capable of adjusting relative distance are arranged beside a piston at the piston extending end of the hydraulic cylinder 24; wherein the adjustable farthest distance of the inductive proximity switch is the maximum extending position of the piston head of the hydraulic cylinder.
The fault simulation method and the test device thereof for the plunger pump under multiple working conditions are further described by combining the embodiment in the following:
the fault simulation method for the plunger pump under multiple working conditions is further explained in detail by taking a certain type of swash plate type axial variable plunger pump as an example.
In the embodiment, the displacement of the swash plate type axial variable plunger pump is 8mL/r, the rated pressure is 21MPa, and the rotating speed range is 500-2000 r/min. Three friction pairs of the swash plate type axial plunger pump are respectively as follows: the plunger is connected with the cylinder hole, the sliding shoe, the swash plate, the port plate and the cylinder port end face. And performing wear fault simulation on the three friction pairs. Because the shaft of the plunger pump 7 is connected with the plunger pump driving motor 8, the plunger pump can keep rotating at high speed and bear torque in work, and therefore the bearing is also a fault-prone component, and fault simulation is carried out on the bearing.
S1, collecting test data of a swash plate type axial variable plunger pump in a normal state, and respectively setting the type x of a temperature state T =3, pressure state type x p =3, traffic status type x q =3, sampling frequency type x s =2, fault type x e Number of failure levels x and =5 g And =3, and the data type K is calculated according to the type expression of the experimental data.
When in the normal state:
K＝x T ·x p ·x q ·x s ＝3×3×3×2＝54；
when a single fault condition, i.e., n =1:
when the composite fault category number n = 2:
when the composite fault category number n = 3:
s11, starting a plunger pump hydraulic system, and enabling the two-position two-way electromagnetic directional valve 19 to be powered on and the three-position four-way electromagnetic directional valve 22 to be in a middle position after the swash plate type axial variable plunger pump runs stably in the system, so that the plunger pump hydraulic system is in a variable load oil way.
S12, designing a test working condition, setting the temperature to be 20-30 ℃, 30-40 ℃ and 40-50 ℃ by matching the running-in preset time of the swash plate type axial variable plunger pump with the fan cooler 21, setting the pressure of the proportional overflow valve 15 to be 4MPa, 8MPa and 12MPa, setting the flow of the proportional throttle valve 18 to be 4L/min, 6L/min and 8L/min, and setting the sampling frequency to be 15kHz and 25kHz, namely, collecting 54 groups of data in each state. Under the conditions of sampling time 5s, sampling times 10 times and sampling interval 1min every time, acquiring acceleration sensor data of a plunger pump shell in X, Y and Z directions and data of a flowmeter, a pressure sensor 13, a temperature sensor 17 and a sound level meter under the normal state of the swash plate type axial variable plunger pump in a variable load oil way, and providing a large amount of data support for multi-sensor data fusion fault diagnosis.
And S13, the electromagnets at the two ends of the three-position four-way electromagnetic directional valve 22 are alternately electrified by powering off the two-position two-way electromagnetic directional valve 19, so that the plunger pump hydraulic system is positioned in a hydraulic impact oil path.
And S14, repeating the numerical setting of the temperature, the pressure, the flow and the sampling frequency in the step S12, fixing the relative positions of two inductive proximity switches positioned at the rod end of the hydraulic cylinder 24, and acquiring the data of acceleration sensors of a plunger pump shell in the X direction, the Y direction and the Z direction and the data of a flow meter, a pressure sensor 13, a temperature sensor 17 and a sound level meter and recording the reversing times of a piston under the conditions that the sampling time is 5S, the sampling times are 10 times and the sampling interval is 1min and the swash plate type axial variable plunger pump in a hydraulic impact oil path is in a normal state.
S2, collecting test data of the plunger pump 7 in a multi-working-condition fault state.
S21, simulating single faults or composite faults of the swash plate type axial plunger pump according to the optimized design, considering the abrasion loss, the damage degree and the shoe loosening degree of different internal elements according to the fault type of the swash plate type axial plunger pump, and setting fault grades of different degrees.
The specific implementation process comprises the following steps:
single failure: according to the operating characteristics of the swash plate type axial plunger pump, the wear of a sliding shoe, the wear of a plunger, the fault of a loose shoe, the wear of a valve plate and the fault of a rolling bearing are respectively set.
Simulation of slipper wear: the surface roughness of the shoe pair was graded stepwise, and the degree of shoe wear was represented by the surface roughness as Ra =0.8, ra =1.6, and Ra =3.2, respectively.
Simulation of plunger wear: since the plunger reciprocates between the cylinder bores, the wear is also the main cause of plunger pump leakage flow, and if the shear flow generated by the plunger motion is not considered and a laminar flow is assumed, the leakage amount at each plunger seal gap is proportional to the third power of the seal gap and the first power of the seal length. The seal clearance is usually about 0.5% of the plunger diameter and 10 to 15 μm, and from the viewpoint of ease of operation, it is proposed to express the degree of wear failure of the plunger by the mass reduction of the plunger, which is 0.10g,0.20g and 0.30g, respectively.
Simulation of shoe loosening failure: the degree of shoe loosening failure is expressed by the amount of clearance between the shoe and the plunger head, which is 0.20mm,0.30mm and 0.40mm, respectively, from the ball head to the shoe.
Simulation of valve plate wear: the wear degree of the port plate is expressed by the maximum wear amount, which is 0.05mm,0.1mm and 0.15mm respectively.
Simulation of rolling bearing failure: the single failure of the three failures is made by damaging the inner ring, the outer ring and the rolling body of the bearing.
Compound failure: and the single faults are combined to realize composite fault simulation.
Specifically, the specific implementation process for the simulation of the shoe wear in a single fault is as follows:
the method comprises the steps of increasing the surface roughness value of a first abrasion grade of a slipper with the surface roughness of Ra =0.1 to Ra =0.8 by using sand paper, installing the slipper into a swash plate type axial variable plunger pump, and adsorbing a magnetic acceleration sensor selected in a test on a pump shell of the swash plate type axial variable plunger pump.
And S22, starting the plunger pump driving motor 8, and running in the fault swash plate type axial variable plunger pump for a period of time according to the oil temperature and the fault type.
And S23, when the fault swash plate type axial variable plunger pump operates stably in the hydraulic system, the two-position two-way electromagnetic directional valve 19 is electrified, and the three-position four-way electromagnetic directional valve 22 is in a neutral position when being electrified.
S24, in order to ensure comprehensiveness of the test data, 5 types of test data such as vibration data, temperature data, flow data, pressure data, and sound data are collected in the present embodiment, wherein in order to more accurately measure vibration data of a bearing fault of the swash plate type axial variable plunger pump, an acceleration sensor is added to an oil filling port sealing screw on a swash plate type axial variable plunger pump housing close to a rolling bearing in the pump, so as to form a four acceleration sensor collection system, and other acceleration sensors are respectively installed in a horizontal direction (X direction), a vertical direction (Y direction), and an axial direction (Z direction) of the pump housing, and are installed perpendicularly to each other two by two on the pump housing of the swash plate type axial variable plunger pump.
S241, respectively setting the proportional throttle valve 18 and the proportional overflow valve 15 through LabVIEW software to enable the flow rate of the system to be 4L/min and the pressure to be 4MPa, simultaneously setting the sampling frequency to be 15kHz and the sampling time to be 5S, sampling times for 10 times under the same condition and sampling interval to be 1min, simultaneously observing the temperature of the oil heated by the thermometer 4 to 20 ℃, simulating the sliding shoe abrasion fault under the working condition, and respectively collecting data of the first flowmeter 3, the second flowmeter 9, the third flowmeter 10, the pressure sensor 13, the temperature sensor 17, the acceleration sensor and the sound level meter by using a data collection system.
And S242, repeating the step S241, and collecting data of the sound level meter, the flow meter, the pressure sensor 13, the temperature sensor 17 and the acceleration sensor under the condition that the sampling frequency is 25 kHz.
And (3) continuously increasing the surface roughness value of the slipper with the surface roughness of Ra =0.8 to Ra =1.6 by using sand paper, installing the slipper into the swash plate type axial variable plunger pump, and adsorbing the magnetic absorption acceleration sensor selected in the test on a pump shell of the swash plate type axial variable plunger pump. And setting different operation parameters according to the operation parameter adjusting method, and repeating the steps S22-S24. And similarly, simulating the fault when the sliding shoe Ra =3.2, and repeating the steps S22-S24, so as to finish the sliding shoe fault simulation test of the swash plate type axial variable plunger pump.
Specifically, the specific implementation process of the composite fault simulation combining the plunger pump bearing and the plunger fault is as follows:
and replacing a supporting rolling bearing of the swash plate type axial variable plunger pump with a bearing with a fault inner ring, and simultaneously replacing a normal plunger with a fault plunger with the mass of the plunger reduced by 0.10 g.
And S22, starting the plunger pump driving motor 8, and running in the fault swash plate type axial variable plunger pump for a period of time according to the oil temperature and the fault type.
And S23, when the fault swash plate type axial variable plunger pump runs stably in the hydraulic system, the two-position two-way electromagnetic directional valve 19 is electrified, and the three-position four-way electromagnetic directional valve 22 is in a neutral position when being electrified.
S24, in order to ensure comprehensiveness of the test data, 5 types of test data such as vibration data, temperature data, flow data, pressure data, and sound data are collected in the present embodiment, wherein in order to more accurately measure vibration data of a bearing fault of the swash plate type axial variable plunger pump, an acceleration sensor is added to an oil filling port sealing screw on a swash plate type axial variable plunger pump housing close to a rolling bearing in the pump, so as to form a four acceleration sensor collection system, and other acceleration sensors are respectively installed in a horizontal direction (X direction), a vertical direction (Y direction), and an axial direction (Z direction) of the pump housing, and are installed perpendicularly to each other two by two on the pump housing of the swash plate type axial variable plunger pump.
S241, respectively setting a proportional throttle valve 18 and a proportional overflow valve 15 through LabVIEW software to enable the flow rate of a system to be 4L/min and the pressure to be 4MPa, simultaneously setting the sampling frequency to be 15kHz and the sampling time to be 5S, sampling times for 10 times under the same condition and sampling interval to be 1min, simultaneously observing a composite fault that when the oil temperature is increased to 20 ℃ by a thermometer 4, the damage of a bearing inner ring and the mass of a plunger are reduced by 0.10g, and respectively acquiring data of a first flowmeter 3, a second flowmeter 9, a third flowmeter 10, a pressure sensor 13, a temperature sensor 17, an acceleration sensor and a sound level meter by using a data acquisition system.
And S242, repeating the step S241, and collecting data of the sound level meter, the flow meter, the pressure sensor 13, the temperature sensor 17 and the acceleration sensor under the condition that the sampling frequency is 25 kHz.
Next, the conditions of other different operating parameters in this failure mode are simulated. Replacing a fault plunger with the plunger mass reduced by 0.20g, setting different operation parameters according to an operation parameter adjusting method, enabling the temperature to exceed a set simulation range in a continuous simulation test, starting a fan cooler 21 for cooling, and repeating the steps S22-S24; in the same manner, the failure simulation is performed when the plunger mass is reduced by 0.30g, and steps S22 to S24 are repeated. And completing the simulation test of the faults of the inner ring of the bearing of the plunger pump and the plunger.
S25, recording delta q of the first flowmeter 3 and q of the second flowmeter 9 and the third flowmeter 10 in corresponding time at 10 sampling times according to the data collected in the step S24 1 And q is 2 And calculating the volumetric efficiency of the swash plate type axial variable plunger pump with different faults in different fault types, and summarizing the results to obtain that the volumetric efficiency is lower along with the increase of the damage degree of the internal components of the plunger pump under the same other conditions.
S26, setting an overflow pressure value of the proportional overflow valve 15 and a flow value of the proportional throttle valve 18, fixing the relative distance between the two inductive proximity switches, starting the normal plunger pump driving motor 8, running for a certain time to enable the temperature to reach a simulation temperature, enabling the two-position two-way electromagnetic directional valve 19 to be de-energized, enabling the electromagnet at the left end of the three-position four-way electromagnetic directional valve 22 to be energized, enabling the piston of the hydraulic cylinder 24 to be in an extending state, enabling the electromagnet at the right end of the three-position four-way electromagnetic directional valve 22 to be energized and enabling the directional valve to be in a right position when the piston head of the hydraulic cylinder 24 triggers the inductive proximity switch with a longer distance, and completing simulation of hydraulic load impact at the moment when the piston of the hydraulic cylinder 24 is switched between extending and contracting.
And S27, repeating the numerical setting of the temperature, the pressure, the flow and the sampling frequency in the step S1, acquiring acceleration sensor data of a plunger pump shell along the X direction, the Y direction and the Z direction and data of a flow meter, a pressure sensor 13, a temperature sensor 17 and a sound level meter under the fault state of the swash plate type axial variable plunger pump in the hydraulic impact oil way each time on the premise of certain sampling time, sampling times and sampling intervals, and recording the piston reversing times.
And S3, taking the data collected in S1 and S2 as original data and storing the original data.
The above-mentioned embodiments are merely illustrative of the preferred embodiments of the present invention, and do not limit the scope of the present invention, and various modifications and improvements made to the technical solution of the present invention by those skilled in the art without departing from the spirit of the present invention shall fall within the protection scope defined by the claims of the present invention.
Claims (3)
1. A fault simulation method for a plunger pump under multiple working conditions is characterized by being based on a multiple fault simulation test device, wherein the multiple fault simulation test device comprises an oil tank, an oil absorption filter, a flowmeter, a thermometer, an air filter, a liquid level meter, the plunger pump, a plunger pump driving motor, a high-pressure filter, a check valve, a pressure sensor, a quick-change connector, a proportional overflow valve, a pressure gauge, a temperature sensor, an oil return filter and a fan cooler, an oil suction port of the plunger pump is connected with a first end of the oil tank through the oil absorption filter, an output end of the plunger pump driving motor is connected with the first end of the plunger pump, the oil drainage end of the plunger pump is connected with the second end of the oil tank through a first flowmeter, the first oil outlet end of the plunger pump is connected with the third end of the oil tank sequentially through a high-pressure filter, a proportional overflow valve and a third flowmeter, the second oil outlet end of the plunger pump is connected with the oil inlet of a proportional throttle valve in a simulation variable load oil path and the oil inlet of a three-position four-way electromagnetic reversing valve in a simulation hydraulic impact oil path in parallel sequentially through an oil inlet of a second flowmeter, a one-way valve, a pressure sensor and a quick-change connector and a temperature sensor, the oil outlet of the quick-change connector is connected with the pressure gauge, and the fourth end, the fifth end and the sixth end of the oil tank are respectively connected with a liquid level meter, an air filter and a thermometer;
the analog variable load oil way further comprises a two-position two-way electromagnetic directional valve, and an oil outlet of the proportional throttle valve is connected with an oil inlet of the two-position two-way electromagnetic directional valve; the simulation hydraulic impact oil way comprises a three-position four-way electromagnetic reversing valve, a first one-way throttle valve, a hydraulic cylinder and a second one-way throttle valve, wherein a first oil outlet of the three-position four-way electromagnetic reversing valve is connected with an oil inlet of the first one-way throttle valve, an oil outlet of the first one-way throttle valve is connected with a rodless end of the hydraulic cylinder, a rod end of the hydraulic cylinder is connected with an oil inlet of the second one-way throttle valve, an oil outlet of the second one-way throttle valve is connected with a second oil outlet of the three-position four-way electromagnetic reversing valve, a third oil outlet of the three-position four-way electromagnetic reversing valve is connected with an oil outlet of the two-position two-way electromagnetic reversing valve in parallel, and the simulation hydraulic impact oil way is connected with a seventh end of an oil tank sequentially through an oil return filter and a fan cooler;
the fault simulation method specifically comprises the following steps:
s1, collecting test data of a plunger pump in a normal state, and establishing a normal state and fault state test data type expression, wherein the specific expression is as follows:
wherein K is the type of experimental data; x is the number of T Is a temperature state type; x is a radical of a fluorine atom p Is a pressure state type; x is the number of q Is a traffic status category; x is the number of s Is a sampling frequency category; x is the number of e Is a fault category; x is the number of g The number of degrees of failure; n is the fault category taken by the composite fault, (n =1,2,3);
the specific implementation process of the step S1 is as follows:
s11, starting a plunger pump hydraulic system, and enabling a two-position two-way electromagnetic directional valve to be electrified and a three-position four-way electromagnetic directional valve to be in a neutral position when the plunger pump runs stably in the system, so that the plunger pump hydraulic system is in a variable-load oil way;
s12, setting test parameters of temperature, pressure, flow and sampling frequency of a test working condition, and acquiring acceleration sensor data of a plunger pump shell in X, Y and Z directions and data of a flowmeter, a pressure sensor, a temperature sensor and a sound level meter in a normal state of the plunger pump in a variable-load oil way on the premise of certain sampling time, sampling times and sampling intervals;
s13, the electromagnets at two ends of the three-position four-way electromagnetic directional valve are alternately powered on by powering off the two-position two-way electromagnetic directional valve, so that the plunger pump hydraulic system is positioned in a hydraulic impact oil way;
s14, fixing the relative positions of two inductive proximity switches positioned at the rod end of the hydraulic cylinder, acquiring acceleration sensor data of a plunger pump shell in X, Y and Z directions and data of a flowmeter, a pressure sensor, a temperature sensor and a sound level meter under the condition that a plunger pump in a hydraulic impact oil way is in a normal state every time on the premise of certain sampling times, sampling intervals and sampling time, and recording piston reversing times;
s2, collecting test data of the plunger pump in a multi-working-condition fault state:
s21, carrying out optimization simulation on single faults or composite faults of the plunger pump, considering the abrasion loss, the damage degree and the shoe loosening degree of different internal elements according to the fault type of the plunger pump, and setting fault grades of different degrees;
s22, starting a plunger pump driving motor, and running in the fault plunger pump according to the oil temperature and the fault type;
s23, when the fault plunger pump runs stably in the hydraulic system, the two-position two-way electromagnetic directional valve is electrified, and the three-position four-way electromagnetic directional valve is in a neutral position when being deenergized;
s24, respectively setting the pressure of a proportional overflow valve and the flow of a proportional throttle valve according to the setting of the pressure, the flow and the temperature of the hydraulic system in the step S1, and setting different temperatures by matching the preset running time of the plunger pump with a fan cooler so that the plunger pumps with different fault levels respectively run once in multiple states of the three conditions of the pressure, the flow and the temperature;
the specific implementation process of the step S24 is as follows:
s241, under the same sampling time, sampling times and sampling interval as those in the step S12, acquiring the sampling frequency ofd 1 Data of a sound level meter, a flow meter, a pressure sensor, a temperature sensor and an acceleration sensor in a kHz state;
s242, repeating the step S241, and collecting the sampling frequency d 2 In a kHz state, data of a sound level meter, a flow meter, a pressure sensor, a temperature sensor and an acceleration sensor;
s25, calculating the volumetric efficiency eta of the plunger pump with different faults in different fault types according to the data collected in the step S24 v Said volumetric efficiency η v The calculation expression of (c) is as follows:
η v ＝(q 1 +q 2 )/(q 1 +q 2 +Δq)
where Δ q is the leakage flow rate of the plunger pump collected by the first flow meter in each failure simulation, q 1 For the flow of the main circuit, q, taken by the second flow meter in the respective time during each fault simulation 2 The overflow flow of the overflow loop collected by the third flow meter in corresponding time in each fault simulation;
s26, after each fault state data acquisition is completed, the two-position two-way electromagnetic directional valve is powered off, and the electromagnet at the left end of the three-position four-way electromagnetic directional valve is powered on, so that the system is connected with a hydraulic impact oil way;
s27, repeating the numerical setting of temperature, pressure, flow and sampling frequency in the step S1, acquiring acceleration sensor data of a plunger pump shell along X, Y and Z directions and data of a flow meter, a pressure sensor, a temperature sensor and a sound level meter in the fault state of the plunger pump when the hydraulic pressure impacts an oil way each time on the premise of certain sampling time, sampling times and sampling intervals, and recording the reversing times of the piston;
and S3, taking the data collected in S1 and S2 as original data and storing the original data.
2. The method for simulating the fault of the plunger pump under the multiple operating conditions as claimed in claim 1, wherein in step S14, the data are collected by each sensor when the piston of the hydraulic cylinder is in normal operation and at the moment of switching the direction.
3. The method for simulating the fault of the plunger pump under the multi-working condition according to claim 1, wherein in step S21, the fault types of the plunger pump comprise the wear amount of each element of a slipper, a plunger and a port plate, the degree of the slipper loosening and the damage degree of an inner ring, an outer ring and a rolling body of a rolling bearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210689129.2A CN115076086B (en) | 2022-06-16 | 2022-06-16 | Fault simulation method and test device for plunger pump under multiple working conditions |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210689129.2A CN115076086B (en) | 2022-06-16 | 2022-06-16 | Fault simulation method and test device for plunger pump under multiple working conditions |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN115076086A CN115076086A (en) | 2022-09-20 |
| CN115076086B true CN115076086B (en) | 2023-03-28 |
Family
ID=83254284
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210689129.2A Active CN115076086B (en) | 2022-06-16 | 2022-06-16 | Fault simulation method and test device for plunger pump under multiple working conditions |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN115076086B (en) |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101413521B (en) * | 2008-11-28 | 2011-05-04 | 西安建筑科技大学 | Experimental apparatus and method for obtaining multi-source diagnostic information of hydraulic equipment |
| CN204921540U (en) * | 2015-09-01 | 2015-12-30 | 浙江大学 | Hydraulic pressure cavitation test system |
| CN105443507B (en) * | 2016-01-08 | 2017-08-01 | 唐山学院 | A kind of Hydraulic System Breakdown simulated experiment platform |
| CN105697353B (en) * | 2016-01-21 | 2017-11-24 | 燕山大学 | A kind of variable working condition Hydraulic pump fault simulation and state-detection combined test apparatus |
| CN110657091B (en) * | 2019-09-20 | 2020-12-11 | 中国农业大学 | Circulating pump bearing fault diagnosis method and system |
| CN111963415A (en) * | 2020-07-15 | 2020-11-20 | 国营芜湖机械厂 | Fault diagnosis method and system for hydraulic plunger pump |
| CN114139297B (en) * | 2021-10-09 | 2024-04-23 | 昆明嘉和科技股份有限公司 | Expert diagnosis system based on machine pump equipment state monitoring and big data analysis |
-
2022
- 2022-06-16 CN CN202210689129.2A patent/CN115076086B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN115076086A (en) | 2022-09-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN111043023B (en) | Fracturing pump on-line monitoring and fault diagnosis system | |
| CN101564831B (en) | Equipment for processing abrasive slurry water-jet microporous nozzle internal runner and method for detecting and controlling real-time flux | |
| CN104775792A (en) | Intelligent oil pumping control method and intelligent oil pumping unit | |
| CN104612631A (en) | Power balance digitization automatic control oil pumping method and oil extraction robot | |
| CN204402438U (en) | Intelligent oil pumping machine | |
| CN105649978A (en) | Device and method for diagnosing faults and testing performance of single-screw pump | |
| CN113008718B (en) | Axial plunger pump flow distribution pair test device and method | |
| CN109058234B (en) | Performance test system and detection method for hydraulic system of electric proportional control valve compensation excavator | |
| CN104405365A (en) | Pumping unit indicator diagram liquid production capacity measurement technology | |
| CN107159964B (en) | Horizontal internal broaching machine intelligence broaching unit | |
| CN110160905A (en) | A kind of variable working condition reciprocating friction and wear testing machine based on double freedom flexible hinge | |
| CN103827505A (en) | Method and system for monitoring the operational state of a pump | |
| CN112347634A (en) | Wind generating set hydraulic variable pitch system fault prediction method based on SCADA system | |
| CN115076086B (en) | Fault simulation method and test device for plunger pump under multiple working conditions | |
| CN110159764B (en) | Intelligent mechanical sealing system and implementation method thereof | |
| CN210397317U (en) | Test device for evaluating performance of hydraulic reciprocating motion sealing piece | |
| CN204402439U (en) | Oil recovery robot | |
| CN112796986B (en) | Cylinder sleeve and piston sealing test device capable of simulating actual operation condition of reciprocating pump | |
| CN112796985B (en) | Piston reciprocating pump cylinder sleeve, piston sealing test device and piston design method | |
| CN109883717A (en) | A kind of cylinder of internal-combustion engine simulator and control method | |
| CN110083962A (en) | A kind of prediction technique and forecasting system of centrifugal pump main shaft service life | |
| CN113984566B (en) | Micro-lubrication-based friction wear machine for comparison test ring block and test method thereof | |
| Almasi | Reciprocating compressor optimum design and manufacturing with respect to performance, reliability and cost | |
| CN210423722U (en) | Intelligent mechanical sealing system | |
| CN208977423U (en) | A kind of lubricant passage way system of machining center |
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 | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |