CN112412927A - Hydraulic element impact fatigue test bench - Google Patents
Hydraulic element impact fatigue test bench Download PDFInfo
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- CN112412927A CN112412927A CN202011160877.9A CN202011160877A CN112412927A CN 112412927 A CN112412927 A CN 112412927A CN 202011160877 A CN202011160877 A CN 202011160877A CN 112412927 A CN112412927 A CN 112412927A
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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
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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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
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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
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of 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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/024—Pressure relief valves
Abstract
The invention belongs to an element impact fatigue test in the field of fluid transmission, and particularly relates to a hydraulic element impact fatigue test bench. The invention adjusts the whole structure of the hydraulic system for fatigue test, separates the working oil path of the control loop from the working oil path of the main test loop through the pilot control structure, and only part of elements on the main test loop are positioned under the test pressure, such as required ultrahigh pressure, and the control loop works at low pressure, thereby easily realizing ultrahigh pressure test. And because all the components of the control circuit work under low pressure, the service life of the control circuit is greatly prolonged; the ultrahigh pressure element can be specially designed in the main loop, so that the maximum test pressure of the test bed can be improved, and the service life of the element in the main loop can be prolonged conveniently. The design of separating the main test loop from the control loop not only prolongs the service life of the whole test bed, but also reduces the test cost of single test.
Description
Technical Field
The invention belongs to an element impact fatigue test in the field of fluid transmission, and particularly relates to a hydraulic element impact fatigue test bench.
Background
Hydraulic component, it is common like pressing the valve, the hydraulic pump, hydraulic motor, hydraulic pressure connects etc. can divide into according to the pressure scope that is suitable for: medium and low voltage components: generally refers to elements with rated working pressure below 21 Mpa; high-voltage element: generally refers to elements with rated service pressure up to 35 Mpa; ultra-high voltage element: generally refers to components rated for service pressures above 35 Mpa. The hydraulic component which is most commonly used in the market at present is a high-pressure hydraulic component, namely a hydraulic component with the rated pressure of 35 MPa.
Hydraulic components are used in hydraulic systems and are often subjected to constant hydraulic shocks. The failure mode is often impact fatigue failure. Therefore, when developing a hydraulic component, the entire component and the pressure receiving member constituting the component are subjected to an impact fatigue test.
Such as: in the most common electromagnetic directional valve, the electromagnetic valve is subjected to a hydraulic impact load every time the electromagnetic valve is reversed. Therefore, when the electromagnetic directional valve is developed, pressure bearing members of the electromagnetic directional valve are as follows: and (4) carrying out 1000 ten thousand times of impact fatigue tests on the valve body and the electromagnetic iron core under the rated pressure of 120%. The solenoid valve as a whole also needs to be subjected to 1000 ten thousand impact fatigue tests (test pressure: 35Mpa × 120% = 42 Mpa).
The hydraulic pump also needs to be subjected to impact fatigue testing during development, and the fatigue testing of the hydraulic pump, particularly the high-pressure plunger pump, is more strict as the working condition of the hydraulic pump is more severe. Therefore, hydraulic impact fatigue testing is critical to the development of hydraulic components.
The trend of hydraulic pressure is toward ultra high pressure systems, which requires that hydraulic components also be developed toward ultra high pressure and be subjected to higher hydraulic impact forces.
This puts very high demands on the test system to provide hydraulic shock: 1. this requires that the test system providing the hydraulic impact test be able to withstand higher pressure impacts than the test element. 2. And higher fatigue life than the test element.
Such as 1000 ten thousand impact fatigue tests for hydraulic valves. After the test is completed, not only the tested piece, but also all the components of the whole test bench are subjected to 1000 ten thousand hydraulic impacts. This makes the impact fatigue test bench need to be overhauled after the test is finished once. Several uses require extensive repair or even replacement of all hydraulic components. This reduces the life of the entire test stand and also increases the cost of a single test.
Disclosure of Invention
The invention aims to overcome the defects and shortcomings of the prior art and provide a hydraulic element impact fatigue test bench.
The technical scheme adopted by the invention is as follows: a hydraulic element impact fatigue test bench comprises a test bench,
the oil tank is used for storing hydraulic oil;
the main test loop is provided with a first hydraulic pump and a main loop main reversing valve main stage, and the first hydraulic pump is connected with the oil tank and inputs test hydraulic pressure to the main test loop;
the control loop is provided with a second hydraulic pump and a main loop main reversing valve control loop control valve, and the second hydraulic pump is connected with an oil tank and inputs pilot control hydraulic pressure to the control loop;
the main loop main reversing valve control loop control valve is a three-position four-way electromagnetic valve, the main loop main reversing valve main stage is a pilot control type, a pilot control cavity of the main loop main reversing valve control loop control valve is connected with the main loop main reversing valve control loop control valve, and when the main loop main reversing valve control loop control valve is switched between power-on and power-off, the main loop main reversing valve main stage outputs square wave impact pressure.
The main test circuit is provided with a main circuit enabling valve, the first hydraulic pump and the main circuit main reversing valve main stage are respectively positioned on two sides of the main circuit enabling valve, the control circuit is provided with a main circuit enabling valve control circuit control valve, the main circuit enabling valve control circuit control valve is a three-position four-way electromagnetic valve, the main circuit enabling valve is of a pilot control type, a pilot control cavity of the main circuit enabling valve control circuit control valve is connected with the main circuit enabling valve control circuit control valve, when the main circuit enabling valve control circuit control valve is powered on, the main circuit enabling valve enables one side of the main circuit main reversing valve main stage to be communicated with one side of the first hydraulic pump, and when the main circuit enabling valve control circuit control valve is powered off, the main circuit enabling valve enables one side of the first hydraulic pump to be communicated with an oil tank for oil return.
The main test loop is provided with a main loop electric proportion pilot overflow valve and a main loop overflow valve which are used for outputting pressure of the main test loop; and the control loop is provided with a control loop electric proportion pilot overflow valve and a control loop overflow valve main stage which are used for controlling the output pressure of the control loop.
The main test circuit is connected with a first hydraulic pump side branch near the output side of the first hydraulic pump, a main circuit pump side diaphragm energy accumulator and a main circuit direct-acting overflow valve are sequentially arranged on the first hydraulic pump side branch, and the main circuit direct-acting overflow valve is communicated with an oil tank.
An oil return pipeline is arranged between the main loop pump side diaphragm energy accumulator and the oil tank, a main loop pump side diaphragm energy accumulator unloading main valve is arranged on the oil return pipeline, a main loop pump side diaphragm energy accumulator unloading main valve pilot electromagnetic valve is arranged on the control loop, the main loop pump side diaphragm energy accumulator unloading main valve pilot electromagnetic valve is a three-position four-way electromagnetic valve, the main loop pump side diaphragm energy accumulator unloading main valve is pilot-controlled, a pilot control cavity of the main loop pump side diaphragm energy accumulator unloading main valve pilot electromagnetic valve is connected with the main loop pump side diaphragm energy accumulator unloading main valve pilot electromagnetic valve, when the main loop pump side diaphragm energy accumulator unloading main valve pilot electromagnetic valve is powered on, the main loop pump side diaphragm energy accumulator is conducted with the oil tank to return oil, and when the main loop pump side diaphragm energy accumulator unloading main valve pilot electromagnetic valve is powered off, a passage between the main loop pump side.
The main test circuit is connected with a main reversing valve side branch circuit close to the main reversing valve main input side of the main test circuit, and a main circuit leather bag energy accumulator is arranged on the main reversing valve side branch circuit.
And a main loop diaphragm energy accumulator is arranged on a side branch of the main reversing valve.
And a main loop check valve is arranged on the main test loop.
One side of the control loop, which is close to the output side of the second hydraulic pump, is connected with a side branch of the second hydraulic pump, a side diaphragm energy accumulator of the control loop pump and a side direct-acting overflow valve of the control loop are sequentially arranged on the side branch of the second hydraulic pump, and the side direct-acting overflow valve of the control loop is communicated with an oil tank.
The control circuit is provided with a control circuit enabling electromagnetic valve, the output is zero pressure when the power is off, and the control circuit is conducted after the power is on.
The invention has the following beneficial effects: the invention adjusts the whole structure of the hydraulic system for fatigue test, separates the working oil path of the control loop from the working oil path of the main test loop through the pilot control structure, and only part of elements on the main test loop are positioned under the test pressure, such as required ultrahigh pressure (such as 60 MPa), and the control loop works at low pressure (such as 10 MPa), thereby easily realizing ultrahigh pressure test. And since all the elements of the control circuit operate at low pressure (10 Mpa), its lifetime is greatly increased; the ultrahigh pressure element can be specially designed in the main loop, so that the maximum test pressure of the test bed can be improved, and the service life of the element in the main loop can be prolonged conveniently. The design of separating the main test loop from the control loop not only prolongs the service life of the whole test bed, but also reduces the test cost of single test.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is within the scope of the present invention for those skilled in the art to obtain other drawings based on the drawings without inventive exercise.
FIG. 1 is a schematic flow chart of an embodiment of the present invention;
in the figure, the position of the upper end of the main shaft,
main test loop constituent element: 1.1, a first hydraulic pump; 1.2, a first hydraulic pump motor; 1.3 a main unloading valve of a diaphragm accumulator at the pump side of the main loop; 1.4, a main loop direct-acting overflow valve; 1.5, a main loop pump side diaphragm accumulator; 1.6, a main loop one-way valve; 1.7 main circuit electric proportion pilot overflow valve; 1.8, a main level of a main loop overflow valve; 1.9, a main circuit enable valve; 1.10, a main loop pressure sensor; 1.11, a main circuit diaphragm accumulator; 1.12, a main loop leather bag energy accumulator; 1.13, a main loop main reversing valve main stage;
control loop constituent elements: 2.1, a second hydraulic pump; 2.2, a second hydraulic pump motor; 2.3, controlling a diaphragm accumulator unloading valve on the pump side of the loop; 2.4, controlling a circuit direct-acting overflow valve; 2.5, controlling a pump side diaphragm accumulator of the loop; 2.6, controlling a one-way valve of a loop; 2.7 controlling the circuit electric proportion pilot overflow valve; 2.8, controlling the main level of an overflow valve of the loop; 2.9, controlling a loop to enable the electromagnetic valve; 2.10, a control loop pressure sensor; 2.11, a main loop enable valve pilot electromagnetic control valve; 2.12, a pilot electromagnetic control valve of a main loop main reversing valve; 2.13, unloading a main valve pilot electromagnetic valve of a main loop pump side diaphragm accumulator;
3.0 and an oil tank.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in further detail with reference to the accompanying drawings.
It should be noted that all expressions using "first" and "second" in the embodiments of the present invention are used for distinguishing two entities with the same name but different names or different parameters, and it should be noted that "first" and "second" are merely for convenience of description and should not be construed as limitations of the embodiments of the present invention, which are not described in any more detail in the following embodiments.
The terms of direction and position of the present invention, such as "up", "down", "front", "back", "left", "right", "inside", "outside", "top", "bottom", "side", etc., refer to the direction and position of the attached drawings. Accordingly, the use of directional and positional terms is intended to illustrate and understand the present invention and is not intended to limit the scope of the present invention.
A hydraulic system of the hydraulic element impact fatigue test bench is designed as shown in figure 1 and comprises an oil tank 3.0, a main test loop and a control loop.
Wherein, the main test circuit includes first hydraulic pump 1.1, main return circuit main reversing valve primary 1.13, first hydraulic pump 1.1 is connected with oil tank 3.0 and is tested hydraulic pressure to main test circuit input, and first hydraulic pump motor 1.2 provides the power supply for first hydraulic pump 1.1.
The hydraulic control system comprises a control loop, wherein a second hydraulic pump 2.1 and a main loop main reversing valve control loop control valve 2.12 are arranged on the control loop, and the second hydraulic pump 2.1 is connected with an oil tank 3.0 to input pilot control hydraulic pressure to the control loop; the second hydraulic pump motor 2.2 provides a power source for the second hydraulic pump 2.1.
The main loop main directional control valve control loop control valve 2.12 is a three-position four-way electromagnetic valve, the main loop main directional valve main stage 1.13 is a pilot control type, a pilot control cavity of the main loop main directional control valve control loop control valve is connected with the main loop main directional valve control loop control valve 2.12, when the main loop main directional valve control loop control valve 2.12 is switched between power-on and power-off, the main loop main directional valve main stage 1.13 outputs square wave impact pressure, when the power-on is conducted, the system high pressure of the main loop is output, when the power-off is conducted, oil return is conducted, and zero pressure is output.
The main test loop is provided with a main loop enabling valve 1.9, the first hydraulic pump 1.1 and a main loop main reversing valve main stage 1.13 are respectively positioned at two sides of the main loop enabling valve 1.9, the control loop is provided with a main loop enabling valve control loop control valve 2.11, the main loop enabling valve control loop control valve 2.11 is a three-position four-way electromagnetic valve, the main loop enabling valve 1.9 is pilot control type, a pilot control cavity of the main loop enabling valve control loop control valve is connected with the main loop enabling valve control loop control valve 2.11, when the main loop enabling valve control loop control valve 2.11 is electrified, the main loop enabling valve 1.9 enables one side of the main loop main reversing valve main stage 1.13 to be communicated with one side of the first hydraulic pump 1.1, and when the main loop enabling valve control loop control valve 2.11 is powered off, the main loop enabling valve 1.9 enables one side of the first hydraulic pump 1.1 to be communicated with an oil tank 3.0. When the electric control loop of the system is suddenly powered off, the pressure output of the system is cut off due to the fact that the enabling valve is also powered off, and safety is guaranteed.
The main test loop is provided with a main loop electric proportion pilot overflow valve 1.7 and a main loop overflow valve main stage 1.8 which are used for outputting pressure of the main test loop, and the main test loop and the main loop overflow valve are matched to realize pressure regulation of the main test loop; and the control loop is provided with a control loop electric proportion pilot overflow valve 2.7 and a control loop overflow valve main stage 2.8 which are used for controlling the output pressure of the control loop, and the control loop electric proportion pilot overflow valve and the control loop overflow valve are matched to realize the pressure regulation of the control loop.
The main test circuit is connected with a first hydraulic pump side branch near the output side of the first hydraulic pump 1.1, a main circuit pump side diaphragm energy accumulator 1.5 and a main circuit direct-acting overflow valve 1.4 are sequentially arranged on the first hydraulic pump side branch, and the main circuit direct-acting overflow valve 1.4 is communicated with an oil tank 3.0. The main loop direct-acting overflow valve 1.4 is a direct-acting overflow valve and has the characteristic of quick response, the opening time is less than 2mS, the pressure impact generated by the pressure fluctuation of the side of a tested piece on the pump side can be reduced, the hydraulic pump is protected, and meanwhile, the main loop direct-acting overflow valve is also used as a main loop safety overflow valve and limits the highest pressure of a main loop, and if the pressure is set to be 61MPa, the pressure is higher than the pressure for overflow protection. The main loop pump side diaphragm accumulator 1.5 is a diaphragm type accumulator and mainly used for absorbing pressure impact transmitted to the pump side by a system, reducing damage of a hydraulic pump caused by the pressure impact, protecting the hydraulic pump and prolonging the service life of the pump.
An oil return pipeline is arranged between the main loop pump side diaphragm energy accumulator 1.5 and the oil tank 3.0, an unloading main valve 1.3 of the main loop pump side diaphragm energy accumulator is arranged on the oil return pipeline, the control loop is provided with a main loop pump side diaphragm energy accumulator unloading main valve pilot electromagnetic valve 2.13, the unloading main valve 2.13 of the main loop pump side diaphragm energy accumulator unloading main valve is a three-position four-way electromagnetic valve, the unloading main valve 1.3 of the main loop pump side diaphragm energy accumulator unloading main valve is a pilot control type, the pilot control cavity is connected with a pilot electromagnetic valve 2.13 of an unloading main valve of a diaphragm energy accumulator at the pump side of a main loop, when the unloading main valve pilot electromagnetic valve 2.13 of the main loop pump side diaphragm energy accumulator is electrified, the main loop pump side diaphragm energy accumulator 1.5 is communicated with the oil tank 3.0 to return oil, when the unloading main valve pilot electromagnetic valve 2.13 of the main loop pump side diaphragm energy accumulator is powered off, a passage between the main loop pump side diaphragm energy accumulator 1.5 and the oil tank 3.0 is disconnected. When the system stops working, the unloading main valve 1.3 of the main circuit pump side diaphragm accumulator is electrified, so that the pressure stored in the main circuit pump side diaphragm accumulator 1.5 can be quickly released.
The main test circuit is connected with a main reversing valve side branch circuit on the side close to the input side of the main stage 1.13 of the main reversing valve of the main circuit, and a main circuit leather bag energy accumulator 1.12 is arranged on the main reversing valve side branch circuit. The main loop leather bag energy accumulator 1.12 mainly plays a role of oil supplement, when the main reversing valve is reversed, a system needs to output pressure oil outwards, the pressure of the main system at the moment of output is pulled down, and at the moment, the energy accumulator outputs high-pressure oil outwards to play a role of supplementing high-pressure oil of a main oil way.
And a main loop diaphragm energy accumulator 1.11 is arranged on a branch of the main reversing valve. The main loop diaphragm accumulator 1.11 is mainly used for absorbing pressure impact generated by switching of the main reversing valve on the side of a tested piece and protecting the whole system.
And a main loop check valve 1.6 is arranged on the main test loop. The instantaneous high-pressure overload on the side of the tested piece is prevented from being transmitted to the pump side, and the hydraulic pump is protected.
The main test loop is also provided with a pressure sensor 1.10 for displaying the pressure of the main loop.
One side of the control loop, which is close to the output side of the second hydraulic pump 2.1, is connected with a second hydraulic pump side branch, a control loop pump side diaphragm energy accumulator 2.5 and a control loop direct-acting overflow valve 2.4 are sequentially arranged on the second hydraulic pump side branch, and the control loop direct-acting overflow valve 2.4 is communicated with an oil tank 3.0. The control loop direct-acting overflow valve 2.4 is a direct-acting overflow valve and has the characteristic of quick response, the opening time is less than 2mS, the pressure impact on the pump side due to system pressure fluctuation can be reduced, the hydraulic pump is protected, in addition, the control loop direct-acting overflow valve can be used as a control loop safety overflow valve, the highest pressure of the control loop is limited, if the pressure is set to be 11MPa, the control loop direct-acting overflow valve is used for overflow protection when the pressure is higher.
An oil return pipeline is arranged between the control circuit pump side diaphragm energy accumulator 2.5 and the oil tank 3.0, an unloading valve 2.3 of the control circuit pump side diaphragm energy accumulator is arranged on the oil return pipeline, the unloading valve 2.3 of the control circuit pump side diaphragm energy accumulator is a general electromagnetic ball valve, when the control circuit pump side diaphragm energy accumulator is electrified, the control circuit pump side diaphragm energy accumulator 2.5 is conducted with the oil tank 3.0 to return oil, and when the control circuit pump side diaphragm energy accumulator is powered off, a passage between the control circuit pump side diaphragm energy accumulator 2.5 and the oil tank 3.0 is disconnected. When the system stops working, the unloading valve 2.3 of the diaphragm accumulator at the pump side of the control circuit is electrified, so that the pressure stored in the diaphragm accumulator 2.5 at the pump side of the control circuit can be quickly released.
And a control loop check valve 2.6 is arranged on the control loop, so that instantaneous high-pressure overload of the system is prevented from being transmitted to the pump side, and a hydraulic pump is protected.
The control loop is provided with a control loop enabling electromagnetic valve 2.9 which is an electromagnetic ball valve, the output of the valve is zero pressure when the valve is powered off, and the control loop is conducted after the valve is powered on.
And a control loop pressure sensor 2.10 is arranged on the control loop and used for displaying the pressure of the control loop.
The working process of the embodiment is as follows:
the second hydraulic pump motor 2.2 of the control loop is started, then the electric proportional pilot overflow valve 2.7 of the control loop is adjusted to set the pressure of the control loop, for example, 10Mpa, and then the control loop enables the electromagnetic valve 2.9 to be electrified. At this time, the pressure output of the pilot control circuit was constant at 10Mpa.
Starting a first hydraulic pump motor 1.2 of a main circuit, then adjusting a main circuit electric proportion pilot overflow valve 1.7 to set the pressure of the main circuit, if the pressure is set to be 60Mpa, then electrifying a left electromagnet of a pilot electromagnetic control valve 2.11 of a main circuit enable valve, opening a main system enable, and then outputting high pressure by the main system.
The left electromagnet of the pilot electromagnetic control valve 2.12 of the main reversing valve of the main loop is continuously switched between power on and power off, so that the pressure output port can output a pressure impact signal of square waves.
When the system stops, the pilot electromagnetic control valve 2.12 of the main loop main reversing valve is powered off, at the moment, the square wave impact pressure is not output from the system output port any more, and the pressure of the main loop output port is zero. Then the pilot electromagnetic control valve 2.11 of the main loop enable valve is cut off, at the moment, the main test loop enable is cut off, and meanwhile, the pressure of the main loop diaphragm accumulator 1.11 and the pressure of the main loop leather bag accumulator 1.12 are released; then the main circuit electric proportion pilot overflow valve 1.7 is adjusted to the lowest pressure. The main circuit main pump outputs a very low pressure at this time. And then the first hydraulic pump motor 1.2 main loop motor is powered off, then the unloading main valve pilot electromagnetic valve of the main loop pump side diaphragm energy accumulator is powered on for 2.13 minutes and then closed, and the pressure of the main loop pump side diaphragm energy accumulator 1.5 energy accumulator is released. After 1 minute, the main circuit was completely closed and there was no longer energy storage.
The control loop enable solenoid valve 2.9 is de-energized, at which time the control loop enable is closed. Then the control loop electric proportional pilot relief valve 2.7 is adjusted to the lowest pressure, at which time the second hydraulic pump 2.1 only outputs a very low pressure. And then the motor of the second hydraulic pump motor 2.2 is powered off, and the unloading valve of the diaphragm accumulator at the pump side of the control loop is powered on for 1 minute by 2.3. And after 1 minute, the unloading valve of the diaphragm accumulator at the pump side of the control loop is cut off 2.3, and at the moment, the control loop system is completely closed, and energy can not be stored any more.
The present embodiment has the following effects:
1. by separating the hydraulic control circuit from the main test circuit, the main test circuit is operated at a high pressure (e.g., 60 Mpa) and the control circuit is operated at a low pressure (e.g., 10 Mpa), thereby facilitating the ultra-high pressure test. And since all the elements of the control circuit operate at low pressure (10 Mpa), its lifetime is greatly increased; the ultrahigh pressure element can be specially designed in the main loop, so that the maximum test pressure of the test bed can be improved, and the service life of the element in the main loop can be prolonged conveniently. The design of separating the main test loop from the control loop not only prolongs the service life of the whole test bed, but also reduces the test cost of single test.
(for example: the test bench is designed to have the maximum test pressure of the main loop of 60Mpa, the control pressure of the control loop is designed to be 10Mpa, the control valve in the main loop is specially designed according to the rated 60Mpa, and the elements in the control loop can be general elements on the market, so that the service life is greatly prolonged because the control valve works at the low pressure of 10 Mpa.)
2. The hydraulic impact in the system is easy to damage the parts in the hydraulic pump such as the plunger, the sliding shoe and the port plate of the hydraulic pump, and the pump is damaged. This embodiment reduces the pressure shock on the pump side due to the abrupt change in the test end pressure by installing a relief valve of a direct-acting type and an accumulator of a diaphragm type on the side close to the pump. The response time of the direct-acting overflow valve is less than 2mS, and the response time of the pilot-type overflow valve is about 10mS, so that the direct-acting overflow valve is more suitable for reducing pressure impact. Meanwhile, the direct-acting overflow valve also plays a role of a safety pressure limiting valve, and when the main electromagnetic pressure regulating valve of the system fails, the direct-acting overflow valve also can play a role of limiting the highest pressure of the main system. Diaphragm accumulators are used primarily to increase the ability to absorb hydraulic shocks. Thus, the hydraulic shock on the pump side is minimized, thereby improving the fatigue life of the hydraulic pump.
3. A diaphragm accumulator and a leather bag type accumulator are arranged on the side of a tested piece. The main function of the leather bag type energy accumulator is oil supplement, so that the system can use a hydraulic pump with smaller flow under the same test flow, and the system cost is reduced. The purpose of the diaphragm accumulator is to absorb pressure shocks from the switching of the reversing valve, reducing pressure pulsations throughout the system.
4. The main hydraulic valves on the main test loop side all adopt a pilot control type. The pilot pressure of which is derived from the control pressure on the control circuit side. At ultra-high pressures, the valve spool hydrodynamic forces due to fluid flow can rise dramatically, requiring significant driving force to open the valve spool. Meanwhile, since the hydrodynamic force varies with the variation of the pressure flow rate, the high pressure causes a decrease in the control accuracy of the control valve. The use of pilot operated hydraulic valves in the main circuit avoids this drawback. The valve core driving force of the pilot valve is derived from hydraulic pressure on two sides of the valve core, and is not directly driven by electromagnetism. The driving force is greatly improved. The control of the main loop is easier and the control precision is improved. Since the pilot control circuit side operates at a low pressure, the control valve may be of an electromagnetic direct-acting type.
5. The whole test system is provided with an enabling valve and an energy accumulator unloading valve in a main loop and a control loop. To improve the security of the whole system. The function of the enabling valve is: in the state where the enable valve is not energized, the entire system has no pressure output, and the system outputs high-pressure oil only when the enable valve is energized. When the electric appliance control loop of the system is suddenly powered off, the pressure output of the system is cut off due to the fact that the enabling valve is also powered off, and safety is guaranteed. The energy accumulator unloading valve has the functions of releasing the pressure of the energy accumulator and releasing the stored energy of the system to zero, so that the safety of the system is ensured.
The above disclosure is only for the purpose of illustrating the preferred embodiments of the present invention, and it is therefore to be understood that the invention is not limited by the scope of the appended claims.
Claims (10)
1. The utility model provides a hydraulic element impact fatigue testboard which characterized in that: comprises the steps of (a) preparing a mixture of a plurality of raw materials,
a tank (3.0) for storing hydraulic oil;
one side of the main test loop is connected with the oil tank (3.0), the other side of the main test loop is used for being connected with a tested piece and outputting impact pressure to the tested piece, a first hydraulic pump (1.1) and a main loop main reversing valve main stage (1.13) are arranged on the main test loop, and the first hydraulic pump (1.1) is connected with the oil tank (3.0) and inputs test hydraulic pressure to the main test loop;
the control circuit is provided with a second hydraulic pump (2.1) and a main circuit main reversing valve control circuit control valve (2.12), and the second hydraulic pump (2.1) is connected with an oil tank (3.0) to input pilot control hydraulic pressure to the control circuit;
the main loop main reversing valve control loop control valve (2.12) is a three-position four-way electromagnetic valve, the main loop main reversing valve main stage (1.13) is in a pilot control type, a pilot control cavity of the main loop main reversing valve control loop control valve is connected with the main loop main reversing valve control loop control valve (2.12), and when the main loop main reversing valve control loop control valve (2.12) is switched between power-on and power-off, the main loop main reversing valve main stage (1.13) outputs square wave impact pressure.
2. The hydraulic component impact fatigue test bench of claim 1, wherein: the main test loop is provided with a main loop enabling valve (1.9), the first hydraulic pump (1.1) and a main stage (1.13) of a main loop main reversing valve are respectively positioned at two sides of the main loop enabling valve (1.9), a main loop enable valve control loop control valve (2.11) is arranged on the control loop, the main loop enable valve control loop control valve (2.11) is a three-position four-way electromagnetic valve, the main loop enable valve (1.9) is of a pilot control type, the pilot control chamber is connected with the main circuit enable valve control circuit control valve (2.11), when the main circuit enable valve control circuit control valve (2.11) is electrified, the main loop enable valve (1.9) is used for communicating one side of a main stage (1.13) of a main loop main reversing valve with one side of a first hydraulic pump (1.1), when the control valve (2.11) of the control loop of the main loop enabling valve is powered off, the main loop enabling valve (1.9) conducts and returns oil for enabling one side of the first hydraulic pump (1.1) to be communicated with the oil tank (3.0).
3. The hydraulic component impact fatigue test bench of claim 1, wherein: the main test loop is provided with a main loop electric proportion pilot overflow valve (1.7) and a main loop overflow valve main stage (1.8) which are used for setting the output pressure of the main test loop; and a control loop electric proportion pilot overflow valve (2.7) and a control loop overflow valve main stage (2.8) which are used for setting the output pressure of the control loop are arranged on the control loop.
4. The hydraulic component impact fatigue test bench of claim 1, wherein: the main test circuit is connected with a first hydraulic pump side branch near the output side of the first hydraulic pump (1.1), a main circuit pump side diaphragm energy accumulator (1.5) and a main circuit direct-acting overflow valve (1.4) are sequentially arranged on the first hydraulic pump side branch, and an overflow port of the main circuit direct-acting overflow valve (1.4) is communicated with an oil tank (3.0).
5. The hydraulic component impact fatigue test bench of claim 4, wherein: an oil return pipeline is arranged between the main loop pump side diaphragm energy accumulator (1.5) and the oil tank (3.0), a main loop pump side diaphragm energy accumulator unloading main valve (1.3) is arranged on the oil return pipeline, a main loop pump side diaphragm energy accumulator unloading main valve pilot solenoid valve (2.13) is arranged on the control loop, the main loop pump side diaphragm energy accumulator unloading main valve pilot solenoid valve (2.13) is a three-position four-way solenoid valve, the main loop pump side diaphragm energy accumulator unloading main valve (1.3) is pilot control type, a pilot control cavity of the main loop pump side diaphragm energy accumulator unloading main valve pilot solenoid valve (2.13) is connected with the main loop pump side diaphragm energy accumulator unloading main valve pilot solenoid valve (2.13), when the main loop pump side diaphragm energy accumulator unloading main valve pilot solenoid valve (2.13) is powered on, the main loop pump side diaphragm energy accumulator unloading main valve pilot solenoid valve (1.5) and the oil tank (3.0) are conducted to enable the main loop pump side diaphragm energy accumulator unloading main valve pilot, the passage between the main circuit pump side diaphragm accumulator (1.5) and the oil tank (3.0) is disconnected.
6. The hydraulic component impact fatigue test bench of claim 1, wherein: one side of the main test loop, which is close to the input side of a main stage (1.13) of a main reversing valve of the main loop, is connected with a side branch of the main reversing valve, and a main loop leather bag energy accumulator (1.12) is arranged on the side branch of the main reversing valve.
7. The hydraulic component impact fatigue test bench of claim 6, wherein: and a main loop diaphragm energy accumulator (1.11) is arranged on a branch of the main reversing valve.
8. The hydraulic component impact fatigue test bench of claim 1, wherein: and a main loop check valve (1.6) is arranged on the main test loop.
9. The hydraulic component impact fatigue test bench of claim 1, wherein: one side, close to the output of the second hydraulic pump (2.1), of the control circuit is connected with a second hydraulic pump side branch, a control circuit pump side diaphragm energy accumulator (2.5) and a control circuit direct-acting overflow valve (2.4) are sequentially arranged on the second hydraulic pump side branch, and an overflow port of the control circuit direct-acting overflow valve (2.4) is communicated with an oil tank (3.0).
10. The hydraulic component impact fatigue test bench of claim 1, wherein: and a control loop enabling electromagnetic valve (2.9) is arranged on the control loop, the output is zero pressure when the power is off, and the control loop is conducted after the power is on.
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Application publication date: 20210226 Assignee: TEJI VALVE GROUP Co.,Ltd. Assignor: Wenzhou University Contract record no.: X2023330000105 Denomination of invention: An impact fatigue testing platform for hydraulic components Granted publication date: 20220823 License type: Common License Record date: 20230311 |
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