CN110159616B - Metallurgical hydraulic cylinder performance test system and test method thereof - Google Patents
Metallurgical hydraulic cylinder performance test system and test method thereof Download PDFInfo
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- CN110159616B CN110159616B CN201910528171.4A CN201910528171A CN110159616B CN 110159616 B CN110159616 B CN 110159616B CN 201910528171 A CN201910528171 A CN 201910528171A CN 110159616 B CN110159616 B CN 110159616B
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- 238000011056 performance test Methods 0.000 title claims abstract description 27
- 238000010998 test method Methods 0.000 title abstract description 8
- 238000012360 testing method Methods 0.000 claims abstract description 41
- 238000006073 displacement reaction Methods 0.000 claims abstract description 30
- 238000002474 experimental method Methods 0.000 claims abstract description 22
- 238000005259 measurement Methods 0.000 claims abstract description 21
- 238000000034 method Methods 0.000 claims description 8
- 238000009434 installation Methods 0.000 claims description 4
- 238000009530 blood pressure measurement Methods 0.000 claims description 2
- 230000008602 contraction Effects 0.000 claims description 2
- 238000013461 design Methods 0.000 claims description 2
- 210000001503 joint Anatomy 0.000 claims description 2
- 238000004891 communication Methods 0.000 claims 3
- 239000003921 oil Substances 0.000 description 161
- 239000007788 liquid Substances 0.000 description 8
- 238000005265 energy consumption Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000005096 rolling process Methods 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000001502 supplementing effect Effects 0.000 description 2
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- 229910000831 Steel Inorganic materials 0.000 description 1
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- 238000011161 development Methods 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
- F15B19/007—Simulation or modelling
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
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- Investigating Strength Of Materials By Application Of Mechanical Stress (AREA)
Abstract
The invention relates to a metallurgical hydraulic cylinder performance test system and a test method thereof, wherein the metallurgical hydraulic cylinder performance test system comprises: the experiment hydraulic system and the measurement and control system; the experimental hydraulic system comprises: the system comprises an experimental hydraulic cylinder and a starting pressure control unit, wherein the starting pressure control unit comprises a pressure reducing valve and an oil supply unit, an oil outlet of the pressure reducing valve is communicated with a rodless cavity of the experimental hydraulic cylinder, and an oil inlet of the pressure reducing valve is communicated with the oil supply unit; the measurement and control system comprises a control cabinet, a first displacement sensor and a first pressure sensor, wherein the first displacement sensor and the first pressure sensor are electrically connected with the control cabinet, the first pressure sensor is arranged on an oil outlet pipeline of the pressure reducing valve, and the first displacement sensor is arranged on a piston rod of the experimental hydraulic cylinder. By the test method of the metallurgical hydraulic cylinder performance test system, the starting pressure of the hydraulic cylinder can be accurately measured, and the test report quality is improved.
Description
Technical Field
The invention relates to the field of hydraulic cylinder performance test, in particular to a metallurgical hydraulic cylinder performance test system and a metallurgical hydraulic cylinder performance test method.
Background
The metallurgical hydraulic cylinder is a key executive component in an electrohydraulic servo system of core equipment of an iron and steel enterprise, is core equipment of a hydraulic AGC system of a current rolling mill, has a series of characteristics of large rolling force, short stroke, high frequency response, high test difficulty and the like when the rolling servo cylinder works, is widely applied to the metallurgical industry, and the performance of the metallurgical hydraulic cylinder directly influences the reliability of the system and the normal operation of production equipment.
In order to reduce the failure rate of production equipment and save maintenance cost. When the product is shipped and repaired, test reports of the performance parameters are required to be attached, and only the performance parameters reach the specified requirements, the product can be approved for use.
Conventional hydraulic cylinder test systems often employ load-on-top cylinders, both cylinders on top of which require high pressure from a hydraulic pump to ensure the required pressure. The high energy consumption caused by the method is always a difficult problem which plagues the testing work of the hydraulic cylinder.
Traditional hydraulic cylinder test systems often employ relief valve control to control the pre-valve pressure to set a lower system pressure to achieve a minimum start-up pressure test. However, in practice, the relief valve is limited by the structural form, which often results in reduced setting accuracy at zero position, and is prone to pressure abrupt change, and finally results in failure of the test system to obtain an accurate pressure value.
The hydraulic cylinder testing system designed by the prior art has the defects of simple structure, low pressure setting precision and high energy consumption, and can not meet the testing requirements of metallurgical hydraulic cylinders.
Disclosure of Invention
The invention provides a metallurgical hydraulic cylinder performance test system and a test method thereof, which can accurately measure the starting pressure of a hydraulic cylinder and solve the problems in the prior art.
The technical scheme adopted by the invention for solving the technical problems is as follows:
a metallurgical hydraulic cylinder performance testing system, comprising: the experiment hydraulic system and the measurement and control system;
The experimental hydraulic system comprises: the system comprises an experimental hydraulic cylinder and a starting pressure control unit, wherein the starting pressure control unit comprises a pressure reducing valve and an oil supply unit, an oil outlet of the pressure reducing valve is communicated with a rodless cavity of the experimental hydraulic cylinder, and an oil inlet of the pressure reducing valve is communicated with the oil supply unit;
The measurement and control system comprises a control cabinet, a first displacement sensor and a first pressure sensor, wherein the first displacement sensor and the first pressure sensor are electrically connected with the control cabinet, the first pressure sensor is arranged on an oil outlet pipeline of the pressure reducing valve, and the first displacement sensor is arranged on a piston rod of the experimental hydraulic cylinder.
Preferably, the oil supply unit includes: the oil tank, constant delivery pump and proportioning pump, the oil inlet of constant delivery pump with the oil inlet of proportioning pump is linked together with the oil tank respectively, the oil-out of constant delivery pump with the oil-out of proportioning pump is linked together with the oil inlet of relief pressure valve respectively, just the constant delivery pump passes through a variable frequency motor drive, the proportioning pump passes through a common motor drive.
Preferably, the metallurgical hydraulic cylinder performance test system further comprises a loading hydraulic system;
The loading hydraulic system includes: the loading hydraulic cylinder and the experimental hydraulic cylinder are arranged in a butt joint manner, and the loading oil circuit is connected with the loading hydraulic cylinder to adjust the hydraulic pressure in a rod cavity and a rodless cavity of the loading hydraulic cylinder;
the experiment hydraulic system further comprises a pressurizing unit, and the pressurizing unit is connected with the experiment hydraulic cylinder to drive the expansion and contraction of a piston rod of the experiment hydraulic cylinder;
The measurement and control system further comprises a tension pressure sensor, and the tension pressure sensor is arranged between the experiment hydraulic cylinder and the loading hydraulic cylinder.
Preferably, the pressurizing unit comprises a servo valve, the servo valve and the pressure reducing valve are arranged in parallel, and the servo valve is electrically connected with the control cabinet.
Preferably, the port A and the port B of the servo valve are respectively communicated with a rodless cavity and a rod cavity of the experimental hydraulic cylinder, the port P of the servo valve is respectively communicated with oil outlets of the constant delivery pump and the proportional pump, and the port T of the servo valve is communicated with the oil tank.
Preferably, the loading oil path includes:
The overflow valve is connected with the oil tank;
the oil inlet of the first one-way valve is communicated with the rodless cavity of the loading hydraulic cylinder, the oil outlet of the first one-way valve is communicated with the oil inlet of the overflow valve, and the oil outlet of the overflow valve is communicated with the oil tank;
The oil inlet of the second one-way valve is communicated with the rod cavity of the loading hydraulic cylinder, and the oil outlet of the second one-way valve is communicated with the oil inlet of the overflow valve;
the oil outlet of the third one-way valve is communicated with the rodless cavity of the loading hydraulic cylinder;
The oil outlet of the fourth one-way valve is connected with the rod cavity of the loading hydraulic cylinder;
The oil outlet of the third hydraulic pump is respectively communicated with the oil inlet of the third check valve and the oil inlet of the fourth check valve, the oil inlet of the third hydraulic pump is communicated with the oil tank, and the third hydraulic pump is driven by a third motor.
Preferably, the measurement and control system further comprises a second pressure sensor, a third pressure sensor and a fourth pressure sensor which are connected with the control cabinet, wherein the second pressure sensor is arranged at the oil inlet of the overflow valve, the third pressure sensor is arranged at the rodless cavity oil port of the loading hydraulic cylinder, and the fourth pressure sensor is arranged at the rod cavity oil port of the loading hydraulic cylinder.
Preferably, the metallurgical hydraulic cylinder performance test system further comprises an internal leakage test unit connected with the experimental hydraulic cylinder, and the internal leakage test unit comprises: the oil inlet of the first electromagnetic ball valve is communicated with the rodless cavity of the experimental hydraulic cylinder, the oil inlet of the second electromagnetic ball valve is communicated with the rod cavity of the experimental hydraulic cylinder, the leakage measuring element is respectively connected with the oil outlet of the first electromagnetic ball valve and the oil outlet of the second electromagnetic ball valve, and the first electromagnetic ball valve and the second electromagnetic ball valve are electrically connected with the control cabinet.
The leakage amount measuring element can adopt the following structure, specifically, a measuring cup can be adopted, the measuring cup is placed on an electronic balance, an oil outlet of a first electromagnetic ball valve and an oil outlet of a second electromagnetic ball valve are communicated with the measuring cup, oil flowing into the measuring cup is weighed through a celestial balance, and then the value of the oil leakage amount in the oil can be obtained; the leakage amount measuring element can also adopt a third hydraulic cylinder, a rod cavity and a rodless cavity of the third hydraulic cylinder are respectively connected with an oil outlet of the first electromagnetic ball valve and an oil outlet of the second electromagnetic ball valve, and a second displacement sensor is further arranged on a piston rod of the third hydraulic cylinder. When the hydraulic oil pump is used, oil is introduced into the rodless cavity of the experimental hydraulic cylinder, the second electromagnetic ball valve is connected at the moment, and liquid oil in the rodless cavity leaks into the third hydraulic cylinder through the oil way, so that a piston rod of the third hydraulic cylinder is displaced, and the leakage amount of the experimental hydraulic cylinder can be calculated through the displacement of the piston rod and the inner diameter of the cylinder body, wherein the inner diameter of the cylinder body of the third hydraulic cylinder is far smaller than that of the experimental hydraulic cylinder. The test mode is not more accurate than the measuring cup test mode because of the error of the third hydraulic cylinder.
Preferably, the metallurgical hydraulic cylinder performance test system may further connect a plurality of second loading hydraulic cylinders of different types in parallel, and when in test use, the second experimental pressure measuring cylinder of a certain type is matched to the corresponding second loading hydraulic cylinder for test, specifically, the rodless cavity and the rod cavity of the second experimental hydraulic cylinder are respectively connected with the port A and the port B of the servo valve, the rodless cavity of the second loading hydraulic cylinder is connected with the oil inlet of the second check valve and the oil outlet of the fourth check valve, and the rod cavity of the second loading hydraulic cylinder is connected with the oil inlet of the first check valve and the oil outlet of the third check valve, so arranged for testing the experimental hydraulic cylinders of different types.
A test method of a metallurgical hydraulic cylinder performance test system comprises the following steps:
(1) Starting a pressure measurement test:
Starting an oil supply unit under an idle state of the experimental hydraulic cylinder, then adjusting a pressure reducing valve on a connecting pipeline of the experimental hydraulic cylinder and the oil supply unit, then manually gradually adjusting the valve opening of the pressure reducing valve, transmitting a displacement signal to a control cabinet when the first displacement sensor starts to generate the displacement signal, and recording the numerical value of the first pressure sensor by the control cabinet, wherein the numerical value is the starting pressure value of the experimental hydraulic cylinder;
(2) Durability measurement test:
under the opposite installation state of the loading hydraulic cylinder and the experimental hydraulic cylinder, the oil supply unit is started, so that the experimental hydraulic cylinder runs at a set value not lower than the design of the tension pressure sensor, and after the experimental hydraulic cylinder runs continuously for a period of time, the accumulated stroke of the experimental hydraulic cylinder is recorded through the measurement and control system.
Specifically, the operation process of loading the hydraulic cylinder in the step (2) under a single operation stroke, namely in a single expansion process, is as follows:
When the port A and the port P of the servo valve are communicated, the oil supply unit continuously supplies oil to the rodless cavity of the experimental hydraulic cylinder, when the piston rod of the experimental hydraulic cylinder pushes the piston rod of the loading hydraulic cylinder to move, the pressure in the rodless cavity of the loading hydraulic cylinder is gradually increased, when the pressure is increased to be higher than the set pressure of the overflow valve, oil in the rodless cavity flows through the overflow valve through the first one-way valve and then flows back to the oil tank, at the moment, because the pressure in the rodless cavity of the loading hydraulic cylinder is higher, the third one-way valve is in a closed state, the third hydraulic pump conveys the oil to the rodless cavity of the loading hydraulic cylinder through the fourth one-way valve, meanwhile, the pressure in the rodless cavity of the experimental hydraulic cylinder is increased, and the oil in the rodless cavity flows back to the oil tank through the port B and the port T of the servo valve;
when the pressure in the rod cavity of the loading hydraulic cylinder is larger than the set pressure of the overflow valve, the control cabinet controls the P port and the B port of the servo valve to be communicated, at the moment, the oil supply unit continuously supplies oil to the rod cavity of the experiment hydraulic cylinder, when the piston rod of the experiment hydraulic cylinder moves reversely, the piston rod of the loading hydraulic cylinder is driven to move reversely, so that the pressure in the rod cavity of the loading hydraulic cylinder is increased, oil in the rod cavity of the loading hydraulic cylinder flows back to the oil tank after sequentially passing through the second one-way valve and the overflow valve, at the moment, the pressure of the rodless cavity of the experiment hydraulic cylinder is increased, the oil in the rodless cavity of the experiment hydraulic cylinder flows back to the oil tank through the A port and the T port of the servo valve, and meanwhile, the third hydraulic pump conveys the oil to the rodless cavity of the loading hydraulic cylinder with reduced pressure through the fourth one-way valve, and the control cabinet controls the A port and the P port of the servo valve to be communicated until the pressure in the rodless cavity of the loading hydraulic cylinder is larger than the set pressure of the overflow valve, and the experiment hydraulic cylinder starts the next single expansion process.
(3) Internal leakage test
Under the opposite installation state of the loading hydraulic cylinder and the experimental hydraulic cylinder, high-pressure liquid oil is injected into a rod cavity of the experimental hydraulic cylinder through an oil supply unit, meanwhile, the first electromagnetic ball valve is closed, the second electromagnetic ball valve is opened, when a piston rod of the experimental hydraulic cylinder moves unidirectionally by a certain displacement b (the displacement b is obtained through a first displacement sensor) within a certain time a, the liquid oil in the experimental hydraulic cylinder flows into a measuring cup through the second electromagnetic ball valve, the liquid oil mass m in the measuring cup is obtained by weighing, and at the moment, if the inner diameter of a cylinder body of the experimental hydraulic cylinder is d, the internal leakage quantity of the experimental hydraulic cylinder in unit time= (m-d b)/a, otherwise, the internal leakage quantity of the experimental hydraulic cylinder in unit time can be measured when the experimental hydraulic cylinder moves reversely.
The invention adopts the structure and has the advantages that: according to the metallurgical hydraulic cylinder performance test system, the pressure reducing valve, the first pressure sensor and the oil supply unit which are connected with the experimental hydraulic cylinder are arranged to be matched for use, so that the accurate measurement of the starting pressure of the hydraulic cylinder is realized, the accuracy of the hydraulic cylinder performance data is improved, the purchaser can select a reliable hydraulic cylinder for use, and the occurrence rate of using faults is reduced.
Through the parallel arrangement of the low-power proportional pump and the low-power quantitative pump, the purpose of providing high-pressure oil liquid for the experimental hydraulic cylinder and the loading hydraulic cylinder is achieved, meanwhile, the lower energy consumption for using the oil supply unit is also achieved, and the energy-saving development concept is met.
Drawings
FIG. 1 is a schematic structural diagram of embodiment 1 of the present invention;
FIG. 2 is a schematic structural diagram of embodiment 2 of the present invention;
fig. 3 is a schematic structural diagram of embodiment 3 of the present invention.
Detailed Description
In order to clearly illustrate the technical features of the present solution, the present invention will be described in detail below with reference to the following detailed description and the accompanying drawings.
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application, but the present application may be practiced in other ways than those described herein, and therefore the scope of the present application is not limited to the specific embodiments disclosed below.
In addition, in the description of the present application, it should be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc. indicate orientations or positional relationships based on the drawings, are merely for convenience in describing the present application and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present application.
Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present application, the meaning of "a plurality" is two or more, unless explicitly defined otherwise.
In the present application, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; the device can be mechanically connected, electrically connected and communicated; can be directly connected or indirectly connected through an intermediate medium, and can be communicated with the inside of two elements or the interaction relationship of the two elements. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art according to the specific circumstances.
In the present application, unless expressly stated or limited otherwise, a first feature "up" or "down" a second feature may be the first and second features in direct contact, or the first and second features in indirect contact via an intervening medium. In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present application. In this specification, schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
Example 1:
As shown in fig. 1, in the present embodiment, the metallurgical hydraulic cylinder performance test system includes an experimental hydraulic system, a loading hydraulic system and a measurement and control system;
The experimental hydraulic system comprises: the hydraulic control system comprises an experimental hydraulic cylinder 1, a starting pressure control unit 2 and a pressurizing unit, wherein the starting pressure control unit 2 comprises a pressure reducing valve 21 and an oil supply unit 22, an oil outlet of the pressure reducing valve 21 is communicated with a rodless cavity of the experimental hydraulic cylinder 1, an oil inlet of the pressure reducing valve 21 is communicated with the oil supply unit 22, the pressurizing unit is connected with the experimental hydraulic cylinder 1 to drive a piston rod of the experimental hydraulic cylinder 1 to stretch out and draw back, the pressurizing unit comprises a servo valve 3, the servo valve 3 can be arranged in parallel with the pressure reducing valve 21, the oil supply unit 22 can be shared, a new oil supply unit can be independently connected, and the servo valve 3 is electrically connected with a control cabinet of a measurement and control system;
The loading hydraulic system includes: the loading hydraulic cylinder 4 and the loading oil circuit 5 are arranged opposite to each other, and the loading oil circuit 5 is connected with the loading hydraulic cylinder 4 to adjust the hydraulic pressure in a rod cavity and a rodless cavity of the loading hydraulic cylinder 4;
the measurement and control system comprises a control cabinet, and a first displacement sensor 7, a first pressure sensor 6 and a tension pressure sensor 8 which are electrically connected with the control cabinet, wherein the first pressure sensor 6 is arranged on an oil outlet pipeline of the pressure reducing valve 21, the first displacement sensor 7 is arranged on a piston rod of the experiment hydraulic cylinder 1, and the tension pressure sensor 8 is arranged between the experiment hydraulic cylinder 1 and the loading hydraulic cylinder 4.
As can be appreciated, the oil supply unit 22 includes: the oil tank 221, the constant delivery pump 222 and the proportional pump 223, wherein the oil inlet of the constant delivery pump 222 and the oil inlet of the proportional pump 223 are respectively communicated with the oil tank 221, the oil outlet of the constant delivery pump 222 and the oil outlet of the proportional pump 223 are respectively communicated with the oil inlet of the pressure reducing valve 21, the constant delivery pump 222 is driven by a variable frequency motor 224, and the proportional pump 223 is driven by a common motor 225;
The port A and the port B of the servo valve 3 are respectively communicated with a rodless cavity and a rod cavity of the experimental hydraulic cylinder 1, the port P of the servo valve 3 is respectively communicated with oil outlets of the constant delivery pump 222 and the proportional pump 223, and the port T of the servo valve 3 is communicated with the oil tank 221.
As can be appreciated, the charging oil passage 5 includes: a relief valve 51, the relief valve 51 being connected to the oil tank 221; the oil inlet of the first one-way valve 52 is communicated with the rodless cavity of the loading hydraulic cylinder 4, the oil outlet of the first one-way valve 52 is communicated with the oil inlet of the overflow valve 51, and the oil outlet of the overflow valve 51 is communicated with the oil tank 221; the oil inlet of the second one-way valve 53 is communicated with the rod cavity of the loading hydraulic cylinder 4, and the oil outlet of the second one-way valve 53 is communicated with the oil inlet of the overflow valve 51; the oil outlet of the third one-way valve 54 is communicated with the rodless cavity of the loading hydraulic cylinder 4; the oil outlet of the fourth one-way valve 55 is connected with the rod cavity of the loading hydraulic cylinder 4; the oil outlet of the third hydraulic pump 56 is respectively communicated with the oil inlet of the third check valve 54 and the oil inlet of the fourth check valve 55, the oil inlet of the third hydraulic pump 56 is communicated with the oil tank 221, and the third hydraulic pump 56 is driven by a third motor 57.
It can be understood that the measurement and control system further comprises a second pressure sensor 9, a third pressure sensor 10 and a fourth pressure sensor 11 which are connected with the control cabinet, wherein the second pressure sensor 9 is arranged at the oil inlet of the overflow valve 51, the third pressure sensor 10 is arranged at the rodless cavity oil port of the loading hydraulic cylinder 4, and the fourth pressure sensor 11 is arranged at the rodless cavity oil port of the loading hydraulic cylinder 4.
A test method of a metallurgical hydraulic cylinder performance test system comprises the following steps:
(1) Test for measuring starting pressure of experimental hydraulic cylinder
Before working, the experimental hydraulic cylinder 1 is in a complete empty load state;
After the system is started, pumping oil into an oil inlet of a pressure reducing valve 21 through a constant displacement pump 222 or/and a proportional pump 223, wherein the servo valve 3 is in a neutral state, namely in a disconnected state, oil enters a rodless cavity of the experimental hydraulic cylinder 1 after passing through the pressure reducing valve 21, then manually adjusting a valve of the pressure reducing valve 21, gradually changing the opening degree of the valve, namely adjusting the pressure after the valve of the pressure reducing valve 21, until a piston rod of the experimental hydraulic cylinder 1 generates displacement, namely when a first displacement sensor 7 starts to generate a displacement signal, transmitting the displacement signal to a control cabinet, and recording the numerical value of the first pressure sensor 6 by the control cabinet, wherein the numerical value is the starting pressure value of the experimental hydraulic cylinder 1;
Compared with the traditional method for controlling the pressure of the system before the valve by adopting the relief valve 51 to determine the lowest starting pressure, the method for directly measuring the pressure after the valve by adopting the relief valve 21 can enable the measurement of the starting pressure to be more accurate, and ensure the quality of the report of the hydraulic cylinder performance test experiment. In particular, for metallurgical cylinders, the starting pressure range is low, about 0.1 mpa, whereas the pressure control range of the relief valve 51 is large, typically varying from a few mpa to a few tens of mpa, which makes it impossible for the relief valve 51 to accurately measure its system pressure and thus to determine its starting pressure.
(2) Durability test
Before working, the end parts of piston rods of the experimental hydraulic cylinder 1 and the loading hydraulic cylinder 4 are relatively installed and fixed, and the pressure reducing valve 21 is closed.
After the system is started, the measurement and control system controls the valve core of the servo valve 3 to move left, so that oil enters the rodless cavity of the experimental hydraulic cylinder 1 through the P port and the A port of the servo valve 3, the internal hydraulic pressure is increased, the piston rod of the experimental hydraulic cylinder 1 is pushed to move right, the hydraulic pressure in the rodless cavity of the loading hydraulic cylinder 4 is increased, and when the hydraulic pressure in the rodless cavity of the loading hydraulic cylinder 4 is increased to be greater than the set pressure of the overflow valve 51 (namely, when the measured pressure value of the third pressure sensor is smaller than the measured pressure value of the second pressure sensor), the oil in the rodless cavity sequentially flows through the first one-way valve 52 and the overflow valve 51 to be introduced into an oil tank. Meanwhile, as the piston rod of the loading hydraulic cylinder 4 moves, the pressure in the rod cavity is lower than the pressure of the oil inlet of the fourth one-way valve 55 (namely, when the measured pressure value of the fourth pressure sensor is smaller than the oil supply pressure of the third hydraulic pump), at the moment, the third motor 57 which always works rotates to drive the third hydraulic pump 56 to work, oil in the oil tank is supplemented into the rod cavity of the loading hydraulic cylinder 1 through the fourth one-way valve 55, the oil supplementing effect is achieved, cavitation phenomenon of the rod cavity of the loading hydraulic cylinder 1 is avoided, and the damage degree of the cavitation phenomenon to the hydraulic cylinder is higher. After the valve core of the servo valve 3 moves leftwards, the port P and the port A of the servo valve 3 are communicated, the port B and the port T are communicated, the oil supply unit 22 continuously supplies oil to the rodless cavity of the experimental hydraulic cylinder 1, when the piston rod of the experimental hydraulic cylinder 1 moves rightwards, the hydraulic pressure in the rod cavity is increased, and the oil in the rod cavity flows back to the oil tank through the port B and the port T of the servo valve 3.
When the hydraulic pressure in the loading hydraulic cylinder is greater than the set pressure of the overflow valve, the measurement and control system controls the valve core of the servo valve 3 to move rightwards, so that the oil enters the rod cavity of the experimental hydraulic cylinder 1 through the P port and the B port of the servo valve 3, the hydraulic pressure in the rod cavity of the experimental hydraulic cylinder 1 is increased, the piston rod of the experimental hydraulic cylinder 1 is pushed to move rightwards, the hydraulic pressure in the rod cavity of the loading hydraulic cylinder 4 is increased, and when the hydraulic pressure in the rod cavity of the loading hydraulic cylinder 4 is increased to be greater than the set pressure of the overflow valve 51 (namely, when the measured pressure value of the fourth pressure sensor is smaller than the measured pressure value of the second pressure sensor), the oil in the rod cavity sequentially flows through the second one-way valve 53 and the overflow valve 51 to be introduced into the oil tank 221. Meanwhile, as the piston rod of the loading hydraulic cylinder 1 moves, the pressure in the rodless cavity is lower than the pressure of the oil inlet of the third one-way valve 54 (namely, when the measured pressure value of the third pressure sensor is smaller than the oil supply pressure of the third hydraulic pump), at the moment, the third motor 57 which always works rotates to drive the third hydraulic pump 56 to work, and the oil in the oil tank is supplemented into the rodless cavity of the loading hydraulic cylinder 4 through the third one-way valve 54, so that the oil supplementing effect is achieved, and the cavitation phenomenon of the rodless cavity of the loading hydraulic cylinder 4 is avoided.
After the servo valve 3 moves right, the port P and the port B of the servo valve 3 are communicated, the port A and the port T are communicated, the oil supply unit 22 continuously supplies oil to the rodless cavity of the experimental hydraulic cylinder 1, when the piston rod of the experimental hydraulic cylinder 1 moves left, the hydraulic pressure in the rod cavity is increased, and the oil in the rod cavity flows back to the oil tank through the port A and the port T of the servo valve 3.
The performance testing system of the metallurgical hydraulic cylinder can accurately test the performance parameters such as the starting pressure, the durability and the like of the hydraulic cylinder; in addition, the oil supply unit supplies oil by adopting a single hydraulic pump, and the consumed current is larger due to larger oil supply flow, so that the energy consumption of the equipment is higher. Compared with a single high-power variable frequency motor or a common motor, the oil supply unit is arranged in such a way that the low-power variable frequency motor and the common motor are used in parallel, the consumed current is smaller, the energy consumption is also smaller, the oil supply unit is used in such a way that the energy is saved, the requirement on working current by using the low-power variable frequency motor and the common motor is lower, the use occasion is wider, the oil supply unit is not easy to be limited by occasion use, and the starting pressure control unit and the supercharging unit share the same oil supply unit, so that the equipment cost can be further saved.
Example 2:
As shown in fig. 2, on the basis of the first embodiment, the metallurgical hydraulic cylinder performance test system further includes an internal leakage test unit connected to the experimental hydraulic cylinder 1, the internal leakage test unit including: the oil inlet of the first electromagnetic ball valve 12 is communicated with the rodless cavity of the experimental hydraulic cylinder 1, the oil inlet of the second electromagnetic ball valve 13 is communicated with the rod cavity of the experimental hydraulic cylinder 1, the leakage amount measuring element 14 is respectively connected with the oil outlet of the first electromagnetic ball valve 12 and the oil outlet of the second electromagnetic ball valve 13, and the first electromagnetic ball valve 12 and the second electromagnetic ball valve 13 are electrically connected with the control cabinet.
The leakage amount measuring element 14 adopts the following structure, specifically, adopts the measuring cup, places the measuring cup on an electronic balance to be linked together with the oil-out of first electromagnetic ball valve and the oil-out of second electromagnetic ball valve, weigh the fluid that flows into the measuring cup through the celestial balance, can obtain the numerical value of the leakage amount in the fluid.
Specifically, the internal leakage test procedure is as follows: in the opposite-top installation state of the loading hydraulic cylinder 4 and the experimental hydraulic cylinder 1, high-pressure liquid oil is injected into a rod cavity of the experimental hydraulic cylinder 1 through an oil supply unit 22, meanwhile, the first electromagnetic ball valve 12 is closed, the second electromagnetic ball valve 13 is opened, when a piston rod of the experimental hydraulic cylinder 1 moves unidirectionally for a certain displacement b (the displacement b is obtained through a first displacement sensor) within a certain time a, the liquid oil in the experimental hydraulic cylinder 1 flows into a measuring cup through the second electromagnetic ball 13 valve, the liquid oil mass m in the measuring cup is obtained by weighing, and at the moment, if the inner diameter of a cylinder body of the experimental hydraulic cylinder 1 is d, the internal leakage amount of the experimental hydraulic cylinder 1 in unit time= (m-d b)/a is obtained, and otherwise, the internal leakage amount of the experimental hydraulic cylinder 1 in unit time without the rod cavity can be measured when the experimental hydraulic cylinder 1 moves reversely.
Example 3:
as shown in fig. 3, on the basis of the second embodiment, the metallurgical hydraulic cylinder performance test system may further connect a plurality of second loading hydraulic cylinders 4.1 of different types in parallel, and when in test use, the second experimental pressure measuring cylinder 1.1 of a certain type is matched to the corresponding second loading hydraulic cylinder 4.1 for test, specifically, the rodless cavity and the rod cavity of the second experimental hydraulic cylinder 1.1 are respectively connected with the port a and the port B of the servo valve 3, the rodless cavity of the second loading hydraulic cylinder 4.1 is connected with the oil inlet of the second check valve 53 and the oil outlet of the fourth check valve 55, and the rod cavity is connected with the oil inlet of the first check valve 52 and the oil outlet of the third check valve 54.
When the performance test is carried out on a large number of hydraulic cylinders, the types of the hydraulic cylinders can be various, and when the hydraulic cylinders are used as experimental hydraulic cylinders for testing, parameters such as the length of a piston rod, the diameter of a cylinder body and the like of the loading hydraulic cylinder need not differ from those of the experimental hydraulic cylinders greatly, so that the single-type loading hydraulic cylinder can only adapt to the performance test of the hydraulic cylinders in a small range. The application can be connected with a plurality of types of loading hydraulic cylinders in parallel so as to adapt to the testing of the hydraulic cylinders in different range sections.
The above embodiments are not to be taken as limiting the scope of the invention, and any alternatives or modifications to the embodiments of the invention will be apparent to those skilled in the art and are intended to fall within the scope of the invention. The present invention is not described in detail in the following, but is well known to those skilled in the art.
Claims (7)
1. A metallurgical hydraulic cylinder performance testing system, comprising: the experiment hydraulic system and the measurement and control system;
The experimental hydraulic system comprises: the system comprises an experimental hydraulic cylinder and a starting pressure control unit, wherein the starting pressure control unit comprises a pressure reducing valve and an oil supply unit, an oil outlet of the pressure reducing valve is communicated with a rodless cavity of the experimental hydraulic cylinder, and an oil inlet of the pressure reducing valve is communicated with the oil supply unit;
The measurement and control system comprises a control cabinet, a first displacement sensor and a first pressure sensor, wherein the first displacement sensor and the first pressure sensor are electrically connected with the control cabinet, the first pressure sensor is arranged on an oil outlet pipeline of the pressure reducing valve, and the first displacement sensor is arranged on a piston rod of the experimental hydraulic cylinder;
the oil supply unit includes: the oil tank, the quantitative pump and the proportional pump are respectively communicated with the oil tank, the oil outlet of the quantitative pump and the oil outlet of the proportional pump are respectively communicated with the oil inlet of the pressure reducing valve, the quantitative pump is driven by a variable frequency motor, and the proportional pump is driven by a common motor;
The metallurgical hydraulic cylinder performance test system further comprises a loading hydraulic system;
The loading hydraulic system includes: the loading hydraulic cylinder and the experimental hydraulic cylinder are arranged in a butt joint manner, and the loading oil circuit is connected with the loading hydraulic cylinder to adjust the hydraulic pressure in a rod cavity and a rodless cavity of the loading hydraulic cylinder;
the experiment hydraulic system further comprises a pressurizing unit, and the pressurizing unit is connected with the experiment hydraulic cylinder to drive the expansion and contraction of a piston rod of the experiment hydraulic cylinder;
the measurement and control system further comprises a tension and pressure sensor, wherein the tension and pressure sensor is arranged between the experiment hydraulic cylinder and the loading hydraulic cylinder;
the metallurgical hydraulic cylinder performance test system further comprises an internal leakage test unit connected with the experimental hydraulic cylinder, wherein the internal leakage test unit comprises: the oil inlet of the first electromagnetic ball valve is communicated with the rodless cavity of the experimental hydraulic cylinder, the oil inlet of the second electromagnetic ball valve is communicated with the rod cavity of the experimental hydraulic cylinder, the leakage measuring element is respectively connected with the oil outlet of the first electromagnetic ball valve and the oil outlet of the second electromagnetic ball valve, and the first electromagnetic ball valve and the second electromagnetic ball valve are electrically connected with the control cabinet.
2. The metallurgical hydraulic cylinder performance test system of claim 1, wherein the booster unit includes a servo valve disposed in parallel with the pressure relief valve and electrically connected to the control cabinet.
3. The metallurgical hydraulic cylinder performance test system of claim 2, wherein port a and port B of the servo valve are respectively in communication with the rodless chamber and the rod-containing chamber of the experimental hydraulic cylinder, port P of the servo valve is respectively in communication with the oil outlets of the dosing pump and the proportional pump, and port T of the servo valve is in communication with the oil tank.
4. The metallurgical hydraulic cylinder performance test system of claim 3, wherein the charge oil circuit comprises: the overflow valve is connected with the oil tank; the oil inlet of the first one-way valve is communicated with the rodless cavity of the loading hydraulic cylinder, the oil outlet of the first one-way valve is communicated with the oil inlet of the overflow valve, and the oil outlet of the overflow valve is communicated with the oil tank; the oil inlet of the second one-way valve is communicated with the rod cavity of the loading hydraulic cylinder, and the oil outlet of the second one-way valve is communicated with the oil inlet of the overflow valve; an oil outlet of the third one-way valve is communicated with a rodless cavity of the loading hydraulic cylinder; the oil outlet of the fourth one-way valve is connected with a rod cavity of the loading hydraulic cylinder; the oil outlet of the third hydraulic pump is respectively communicated with the oil inlet of the third check valve and the oil inlet of the fourth check valve, the oil inlet of the third hydraulic pump is communicated with the oil tank, and the third hydraulic pump is driven by a third motor.
5. The system for testing the performance of the metallurgical hydraulic cylinder according to claim 4, further comprising a second pressure sensor, a third pressure sensor and a fourth pressure sensor which are connected with the control cabinet, wherein the second pressure sensor is arranged at the oil inlet of the overflow valve, the third pressure sensor is arranged at the rodless cavity oil port of the loading hydraulic cylinder, and the fourth pressure sensor is arranged at the rod cavity oil port of the loading hydraulic cylinder.
6. A testing method using the metallurgical hydraulic cylinder performance testing system of claim 5, comprising the steps of:
(1) Starting a pressure measurement test:
Starting an oil supply unit under an idle state of the experimental hydraulic cylinder, then adjusting a pressure reducing valve on a connecting pipeline of the experimental hydraulic cylinder and the oil supply unit, then manually gradually adjusting the valve opening of the pressure reducing valve, transmitting a displacement signal to a control cabinet when the first displacement sensor starts to generate the displacement signal, and recording the numerical value of the first pressure sensor by the control cabinet, wherein the numerical value is the starting pressure value of the experimental hydraulic cylinder;
(2) Durability measurement test:
under the opposite installation state of the loading hydraulic cylinder and the experimental hydraulic cylinder, the oil supply unit is started, so that the experimental hydraulic cylinder runs at a set value not lower than the design of the tension pressure sensor, and after the experimental hydraulic cylinder runs continuously for a period of time, the accumulated stroke of the experimental hydraulic cylinder is recorded through the measurement and control system.
7. The method of claim 6, wherein the test of the test cylinder performance test system in step (2) is performed by the following steps:
When the opening A and the opening P of the servo valve are communicated, the oil supply unit continuously supplies oil to the rodless cavity of the experiment hydraulic cylinder, when the piston rod of the experiment hydraulic cylinder pushes the piston rod of the loading hydraulic cylinder to move, the pressure in the rodless cavity of the loading hydraulic cylinder is gradually increased, when the pressure is increased to be higher than the set pressure of the overflow valve, the oil in the rodless cavity flows through the overflow valve and then flows back to the oil tank through the first one-way valve, at the moment, the pressure in the rodless cavity of the loading hydraulic cylinder is higher, the third one-way valve is in a closed state, the third hydraulic pump conveys the oil to the rodless cavity of the loading hydraulic cylinder through the fourth one-way valve, when the pressure in the rodless cavity of the loading hydraulic cylinder is higher than the set pressure of the overflow valve, the opening P and the opening B of the servo valve are controlled to be communicated, at the moment, the oil supply unit continuously supplies oil to the rodless cavity of the experiment hydraulic cylinder, the pressure in the rodless cavity of the loading hydraulic cylinder is sequentially increased, the oil in the rodless cavity of the loading hydraulic cylinder flows back to the oil tank through the second one-way valve, the pressure in the third one-way valve is conveyed to the rodless cavity of the loading hydraulic cylinder through the fourth one-way valve, and the pressure in the rodless cavity is smaller than the pressure of the rodless cavity, and the pressure is less than the pressure in the single opening A is controlled, and the pressure is smaller than the pressure in the single opening P is controlled.
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| CN113217488B (en) * | 2021-04-21 | 2024-04-26 | 沈阳海瑞琦液压科技有限公司 | System and method for measuring minimum starting pressure of hydraulic cylinder |
| CN113883130A (en) * | 2021-05-08 | 2022-01-04 | 山东金利液压科技有限公司 | Manufacturing method of oil cylinder simulation test combined experiment platform |
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