High-pressure multi-channel multi-field coupling reciprocating dynamic seal comprehensive test system

Abstract

The application relates to the technical field of seal testing, and discloses a high-pressure multi-channel multi-field coupling reciprocating dynamic seal comprehensive test system, which comprises: a plurality of test devices, which are respectively used for mounting seals and performing seal testing on the seals; a main hydraulic energy device connected with the plurality of test devices and used for providing pressure oil with a first flow rate to the test devices within a unit time; and an auxiliary hydraulic energy device connected with the plurality of test devices and used for providing pressure oil with a second flow rate to the test devices within a unit time; wherein the first flow rate is greater than the second flow rate. Through the technical scheme, the technical problem that the high-pressure multi-channel multi-field coupling reciprocating dynamic seal comprehensive test system in the related art cannot independently supply oil according to flow rate requirement differences of various test modules and pressure fluctuation caused by working condition changes of one module is transmitted to other test modules through a shared oil supply pipeline to interfere with seal testing is solved.

Description

Technical Field

[0001] This invention relates to the field of sealing component testing technology, and in particular to a high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system. Background Technology

[0002] The high-pressure multi-channel multi-field coupled hydraulic rubber and plastic reciprocating dynamic seal comprehensive test bench is mainly used for component-level testing of linear reciprocating rubber and plastic seals and hydraulic product-level testing of simulated actuators. It can simulate the test conditions of the test object under actual working conditions to verify the performance and indicators of the test object under different oil source pressures, temperatures and different ambient temperatures, and to verify the reliability of the test object.

[0003] During seal testing, different test modules have varying requirements for oil supply flow. For example, driving a simulated cylinder to perform high-frequency reciprocating motion requires a large oil supply flow, while component-level seal testing only needs to establish pressure within the sealing cavity and has a smaller oil supply flow requirement. Existing technologies using parallel oil supply from a single hydraulic station are difficult to adjust independently according to the different flow requirements of each test module. They often rely on complex flow distribution valve assemblies to achieve flow distribution. Furthermore, changes in the operating conditions of one module (such as pressure fluctuations caused by high-speed reversing of the simulated cylinder) can directly couple to the entire system, interfering with other ongoing tests. Summary of the Invention

[0004] This application discloses a high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system to solve the technical problems existing in related technologies, such as the difficulty in independently supplying oil according to the flow requirements of each test module, and the pressure fluctuations caused by the change of operating conditions of one module being transmitted to other test modules through a shared oil supply pipeline, interfering with the seal test.

[0005] To solve the above problems, the present invention adopts the following technical solution: This application discloses a high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system, including: Multiple testing devices are used to install the seals and perform sealing tests on them. The main hydraulic power unit, connected to multiple testing devices, is used to supply pressurized oil with a first flow rate to the testing devices per unit time; A secondary hydraulic power unit, connected to multiple testing devices, is used to supply pressurized oil with a second flow rate to the testing devices per unit time; The first flow rate is greater than the second flow rate.

[0006] In some schemes, at least one test apparatus includes a simulation fixture and a first test fixture. The simulation fixture is used to test the sealing reliability of the seal under simulated real-world installation conditions, and the first test fixture is used to test the sealing performance of the seal itself under standardized conditions. The main hydraulic power unit is connected to the simulation fixture and the first test fixture, and the auxiliary hydraulic power unit is connected to the first test fixture.

[0007] In some schemes, at least one testing device includes a second test fixture for testing the sealing performance of the seal itself under standardized conditions; The main hydraulic power unit is connected to the second test fixture, and the auxiliary hydraulic power unit is also connected to the second test fixture.

[0008] In some designs, the simulation fixture includes a simulation cylinder and a load spring. The simulation cylinder is used to install the seals, and the load spring is mounted on the piston end of the simulation cylinder. The simulation cylinder is connected to the main hydraulic power unit. And / or, the first test fixture includes a first test cylinder and a first servo electric cylinder. The first test cylinder is used to install the seal. The drive end of the first servo electric cylinder is connected to the piston end of the first test cylinder. The first test cylinder is connected to the main hydraulic power unit and the auxiliary hydraulic power unit. And / or, the second test fixture includes a second test cylinder and a second servo electric cylinder. The second test cylinder is used to install the seal. The drive end of the second servo electric cylinder is connected to the piston end of the second test cylinder. The second test cylinder is connected to the main hydraulic power unit and the auxiliary hydraulic power unit.

[0009] In some schemes, the main hydraulic power unit includes a first oil tank, a first oil inlet pipe, a first oil return pipe, a variable displacement piston pump assembly, and a first heat exchanger. One end of the first oil inlet pipe is connected to the first oil tank through the variable displacement piston pump assembly, and the other end is connected to the simulation fixture through a servo valve. It is also connected to the first test fixture and the second test fixture through a first proportional pressure regulating valve. One end of the first return oil pipe is connected to the first oil tank via the first heat exchanger, and the other end is connected to the simulation fixture via the servo valve, and to the first test fixture and the second test fixture via the proportional relief valve.

[0010] In some designs, the main hydraulic power unit also includes a circulation pipeline, a circulation pump, and a heater. One end of the circulation pipeline is connected to the first oil tank, and the other end is connected to the first return oil pipe through the circulation pump and the heater. And / or, the main hydraulic power unit also includes a first emergency pipe and a first electromagnetic unloading valve, wherein the first emergency pipe is connected to a first oil inlet pipe and a first oil return pipe through the first electromagnetic unloading valve; And / or, the main hydraulic power unit also includes a first accumulator, which is connected to a first oil inlet pipe.

[0011] In some designs, the first inlet pipe has several first spare interfaces; And / or, the first oil inlet pipe has a first sampling port; And / or, the first return line has several second spare interfaces.

[0012] In some designs, the auxiliary hydraulic power unit includes a second oil tank, a second oil inlet pipe, a second oil return pipe, a fixed displacement piston pump assembly, and a second heat exchanger; one end of the second oil inlet pipe is connected to the second oil tank via the fixed displacement piston pump assembly, and the other end is connected to the first test fixture and the second test fixture via a first proportional pressure regulating valve; One end of the second return oil pipe is connected to the second oil tank via the second heat exchanger, and the other end is connected to the first test fixture and the second test fixture via a proportional relief valve.

[0013] In some designs, the second inlet pipe has several third spare interfaces; And / or, the second return line has several fourth spare interfaces; And / or, the second oil inlet pipe has a second sampling port; And / or, the auxiliary hydraulic power unit also includes a second emergency pipe and a second electromagnetic unloading valve, the second emergency pipe being connected to a second oil inlet pipe and a second oil return pipe via the second electromagnetic unloading valve; And / or, the auxiliary hydraulic power unit also includes a second accumulator connected to a second oil inlet pipe.

[0014] In some designs, the auxiliary hydraulic power unit also includes a third emergency pipe and a second proportional pressure regulating valve, with the third emergency pipe connected to the second emergency pipe and the second oil inlet pipe via the second proportional pressure regulating valve. And / or, the capacity of the first fuel tank is greater than the capacity of the second fuel tank.

[0015] The technical solution adopted in this invention can achieve the following beneficial effects: This application discloses a high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system. Multiple test devices are installed with seals and each performs seal tests independently. The main hydraulic power unit supplies pressurized oil with a first flow rate to each test device, and the auxiliary hydraulic power unit supplies pressurized oil with a second flow rate to each test device, where the first flow rate is greater than the second flow rate. Each test device obtains pressurized oil with a corresponding flow rate from the main or auxiliary hydraulic power unit according to the oil supply flow rate required for its own seal test, enabling each test device to complete the test under the oil supply conditions required by the seal being tested. The oil supply lines of the main hydraulic power unit and the auxiliary hydraulic power unit are not connected to each other. Pressure fluctuations in either oil supply system exist only within that system and are not transmitted to the test device connected to the other oil supply system through the oil supply line.

[0016] The main hydraulic power unit and the auxiliary hydraulic power unit supply oil to the test device independently, which solves the problem in the existing single hydraulic station parallel oil supply scheme that makes it difficult to supply oil independently according to the different flow requirements of each test device because different test devices share the same oil source; the pressure fluctuation of any oil supply system will not be transmitted to the test device connected to another oil supply system through the oil supply pipeline, which solves the technical problem in the existing technology that the pressure fluctuation caused by the change of operating conditions of one test device is transmitted to other test devices through the shared oil supply pipeline, interfering with the sealing test. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the structure of the high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system disclosed in some embodiments of this application; Figure 2 This is a schematic diagram of the main hydraulic power device disclosed in some embodiments of this application; Figure 3 This is a schematic diagram of the structure of the auxiliary hydraulic power device disclosed in some embodiments of this application; Figure 4 This is a schematic diagram of the structure of the testing apparatus disclosed in some embodiments of this application. Figure 1 ; Figure 5 This is a schematic diagram of the structure of the testing apparatus disclosed in some embodiments of this application. Figure 2 .

[0019] In the picture: 100-Testing device, 110-Simulation fixture, 111-Simulation cylinder, 112-Load spring, 120-First test fixture, 121-First test cylinder, 122-First servo electric cylinder, 130-Second test fixture, 131-Second test cylinder, 132-Second servo electric cylinder; 200-Main hydraulic power unit, 2010-First oil tank, 2020-First oil inlet pipe, 2030-First oil return pipe, 2040-Variable displacement piston pump set, 2050-First heat exchanger, 2060-Circulation pipeline, 2070-Circulation pump, 2080-Heater, 2090-First emergency pipe, 2100-First electromagnetic unloading valve, 2110-First accumulator, 2120-First backup interface, 2130-First sampling port, 2140-Second backup interface; 300 - Secondary hydraulic power unit; 3010 - Second oil tank; 3020 - Second oil inlet pipe; 3030 - Second oil return pipe; 3040 - Fixed displacement plunger pump assembly; 3050 - Second heat exchanger; 3060 - Third backup interface; 3070 - Fourth backup interface; 3080 - Second sampling port; 3090 - Second emergency pipe; 3100 - Second electromagnetic unloading valve; 3110 - Second accumulator; 3120 - Third emergency pipe; 3130 - Second proportional pressure regulating valve. 10 - Servo valve, 20 - First proportional pressure regulating valve, 30 - Proportional relief valve. Detailed Implementation

[0020] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be described in detail below. Obviously, the described embodiments are merely some embodiments of this invention, and not all embodiments. Based on the embodiments of this invention, all other implementation methods obtained by those skilled in the art without creative effort are within the scope of protection of this invention.

[0021] The terms "first," "second," etc., used in the specification and claims of this application are used to distinguish similar objects and not to describe a specific order or sequence. It should be understood that such use of data can be interchanged where appropriate so that embodiments of this application can be implemented in orders other than those illustrated or described herein, and the objects distinguished by "first," "second," etc., are generally of the same class and the number of objects is not limited; for example, a first object can be one or more. Furthermore, in the specification and claims, "and / or" indicates at least one of the connected objects, and the character " / " generally indicates that the preceding and following objects are in an "or" relationship.

[0022] The following is in conjunction with the appendix Figures 1 to 5 This paper provides a detailed description of a high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system provided in this application through specific embodiments and application scenarios.

[0023] Some embodiments of this application disclose a high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system, including a main hydraulic power unit 200, an auxiliary hydraulic power unit 300, and multiple test devices 100.

[0024] like Figure 1 As shown, the test device 100 is used to install seals and perform sealing tests on the seals; the main hydraulic power unit 200 is connected to multiple test devices 100 and is used to provide pressure oil with a first flow rate to the test devices 100 within a unit time; the auxiliary hydraulic power unit 300 is connected to multiple test devices 100 and is used to provide pressure oil with a second flow rate to the test devices 100 within a unit time.

[0025] Each testing device 100 independently installs and performs sealing tests on its own seals, ensuring that the testing process for each seal is independent and avoiding the inefficiency and inconsistent testing conditions caused by testing multiple seals in turn at the same station. The main hydraulic power unit 200 and the auxiliary hydraulic power unit 300 independently supply oil to the testing device 100, and their oil supply pipelines are not connected. Therefore, pressure fluctuations in either oil supply system exist only within that system and will not be transmitted to the testing device 100 connected to the other system through a shared pipeline, thus avoiding interference from oil supply pressure fluctuations on the sealing test. At the same time, the difference between the first flow rate and the second flow rate provides the conditions for different testing devices 100 to independently supply oil according to the oil supply flow rate required for their own sealing tests.

[0026] In this embodiment, the first flow rate is greater than the second flow rate. The main hydraulic power unit 200 is connected to a simulated actuator cylinder (product-level test module). The simulated actuator cylinder uses hydraulic oil to drive the piston in reciprocating motion to test the performance of the seal under actual working conditions. The reciprocating motion of the piston in the cylinder requires a continuous flow of hydraulic oil in and out of the cylinder. The required flow rate is directly related to the piston's movement speed and piston area, and the required flow rate is greater during high-frequency reciprocating motion. Therefore, the main hydraulic power unit 200 needs to provide a larger first flow rate to meet the oil supply requirements of the simulated actuator cylinder during the reciprocating motion. The auxiliary hydraulic power unit 300 is connected to a test fixture (component-level test module). The test fixture drives the piston rod to reciprocate via an electric cylinder. The hydraulic oil only needs to build pressure in the sealing cavity to simulate a high-pressure environment and does not drive the piston to move. The oil is basically stationary in the cavity and only needs to replenish a small amount of leakage. Therefore, the auxiliary hydraulic power unit 300 only needs to provide a smaller second flow rate to meet the oil pressure requirements of the test fixture.

[0027] like Figure 1 and Figure 4 As shown, at least one testing device 100 includes a simulation fixture 110 and a first test fixture 120. The simulation fixture 110 is used to test the sealing reliability of the seal under simulated real installation conditions, and the first test fixture 120 is used to test the sealing performance of the seal itself under standardized conditions. The main hydraulic power unit 200 is connected to the simulation fixture 110 and the first test fixture 120, and the auxiliary hydraulic power unit 300 is connected to the first test fixture 120.

[0028] When the simulated fixture 110 performs seal testing under simulated real-world installation conditions, its internal components continuously drive the load in reciprocating motion. This process requires the oil supply system to provide a large flow rate of pressurized oil per unit time. The initial flow rate provided by the main hydraulic power unit 200 can meet the oil supply requirements of the simulated fixture 110, therefore the main hydraulic power unit 200 is connected to the simulated fixture 110 to supply oil. When the first test fixture 120 performs seal testing under standardized conditions, its internal piston rod is driven by an electric cylinder. The oil supply system only needs to establish a pressurized oil environment within the sealing cavity and does not participate in driving the piston movement, therefore there is no strict requirement for the oil supply flow rate. The initial flow rate provided by the main hydraulic power unit 200 can also be used to meet this oil supply requirement of the first test fixture 120, therefore the main hydraulic power unit 200 is connected to the first test fixture 120 to supply oil. The second flow rate provided by the auxiliary hydraulic power unit 300 is less than the first flow rate. Its oil supply cannot meet the oil supply requirements of the simulated tooling 110 driving the load to reciprocate, but it can meet the oil supply requirements of the first test tooling 120, which only needs to establish a pressure oil environment and has no strict requirements on the oil supply flow rate. Therefore, the auxiliary hydraulic power unit 300 is connected to the first test tooling 120 to supply oil to it.

[0029] The simulation fixture 110 and the first test fixture 120 share the main hydraulic power unit 200, so that one oil supply system can meet the oil supply needs of multiple test devices 100 at the same time, without the need to configure an independent oil supply system for each test device 100. Furthermore, the auxiliary hydraulic power unit 300 is independently connected to the first test fixture 120, providing the first test fixture 120 with a second oil supply source besides the main hydraulic power unit 200. When the operation of the simulation fixture 110 causes pressure fluctuations in the main hydraulic power unit 200, these fluctuations only exist in the oil supply line of the main hydraulic power unit 200 and will not be transmitted to the first test fixture 120 through the auxiliary hydraulic power unit 300. This avoids interference from changes in the operating conditions of the simulation fixture 110 on the sealing test of the first test fixture 120. At the same time, the main hydraulic power unit 200 and the auxiliary hydraulic power unit 300 provide the first flow rate and the second flow rate to the first test fixture 120, respectively, without affecting each other. When either oil supply device stops supplying oil due to maintenance or malfunction, the other oil supply device can still maintain the sealing test of the first test fixture 120, reducing the risk of test interruption due to the failure of a single oil supply device.

[0030] like Figure 1 and Figure 5 As shown, at least one testing device 100 includes a second testing fixture 130, which is used to test the sealing performance of the seal itself under standardized conditions; a main hydraulic power unit 200 is connected to the second testing fixture 130, and an auxiliary hydraulic power unit 300 is connected to the second testing fixture 130.

[0031] The second test fixture 130 is identical to the first test fixture 120; both are used to test the sealing performance of the seal itself under standardized conditions. There are no strict requirements on the oil supply flow rate; only a pressurized oil environment needs to be established within the sealing cavity. The first flow rate provided by the main hydraulic power unit 200 and the second flow rate provided by the auxiliary hydraulic power unit 300 can both meet the aforementioned oil supply requirements of the second test fixture 130. Therefore, the main hydraulic power unit 200 and the auxiliary hydraulic power unit 300 are respectively connected to the second test fixture 130. The second test fixture 130 receives both the first and second flow rates simultaneously, with each supplying oil to the second test fixture 130 independently.

[0032] Performance testing of seals under standardized conditions is a fundamental means of screening and verifying the basic performance of seals. This test itself has no strict requirements on the oil supply flow rate, only the establishment of a pressurized oil environment is needed. Therefore, the testing requirements can be met by configuring only the second test fixture 130 with at least one test device 100, without the need to set up a simulation fixture 110. The test device 100 without the simulation fixture 110 is specifically used to perform standardized seal tests. This test device 100 operates in parallel with the test device 100 that simultaneously includes the simulation fixture 110 and the first test fixture 120, so that the seal performance test under standardized conditions can be carried out independently of the test simulating the actual installed conditions and is not affected by the operating status of the simulation fixture 110.

[0033] like Figure 4 As shown, the simulation fixture 110 includes a simulation cylinder 111 and a load spring 112. The simulation cylinder 111 is used to install the seal, and the load spring 112 is installed on the piston end of the simulation cylinder 111. The simulation cylinder 111 is connected to the main hydraulic power unit 200. Through the cooperation of the simulation cylinder 111 and the load spring 112, the simulation fixture 110 performs a sealing performance test on the seal installed in the simulation cylinder 111 under the drive of high-pressure oil.

[0034] The simulated cylinder 111 is manufactured according to the actual groove dimensions of the actual installed seal. The seal is installed in the groove, so that the installation structure of the seal during the test is consistent with the actual installed state. The pressure oil supplied by the main hydraulic power unit 200 directly drives the piston movement of the simulated cylinder 111. The load spring 112 is installed at the piston end and applies resistance to the piston during the piston movement that is equivalent to the actual working condition, so that the oil pressure and piston force state inside the simulated cylinder 111 are close to the actual working conditions. The pressure and temperature of the pressure oil provided by the main hydraulic power unit 200, the frequency and stroke of driving the piston reciprocating motion can all be set according to the actual installed working conditions of the seal, so that the oil pressure, oil temperature, reciprocating motion speed and frequency borne by the seal during the test are consistent with the actual installed working conditions. Therefore, the leakage of the seal measured by the simulated fixture 110 can reflect the sealing performance of the seal under the actual installed state.

[0035] The main hydraulic power unit 200 supplies pressurized oil with a first flow rate to the simulated cylinder 111. After entering the simulated cylinder 111, the pressurized oil pushes the piston to move. The load spring 112 installed at the piston end of the simulated cylinder 111 is compressed or stretched during the piston's movement, applying resistance to the piston in the opposite direction of movement, thus increasing the oil pressure inside the simulated cylinder 111 to the test pressure required by the seal. The pressurized oil contacts the seal installed inside the simulated cylinder 111. Under the action of the pressurized oil, the seal deforms and adheres to the inner wall of the simulated cylinder 111. A sealing contact surface is formed on the piston rod surface. The main hydraulic power unit 200 continuously supplies pressurized oil to drive the piston to reciprocate. The seal is always subjected to oil pressure during the piston's reciprocating motion. If the high-pressure oil in the simulated cylinder 111 leaks along the contact surface between the seal and the inner wall of the simulated cylinder 111 or between the piston rod during the piston's movement, the leaked oil will flow out through the leakage collection channel set on the simulated cylinder 111. By measuring the amount of oil flowing out of the leakage collection channel, the leakage amount of the seal under simulated real installation conditions can be obtained, thereby evaluating the sealing performance of the seal.

[0036] like Figure 4 As shown, the first test fixture 120 includes a first test cylinder 121 and a first servo electric cylinder 122. The first test cylinder 121 is used to install the seal. The drive end of the first servo electric cylinder 122 is connected to the piston end of the first test cylinder 121. The first test cylinder 121 is connected to the main hydraulic power unit 200 and the auxiliary hydraulic power unit 300.

[0037] The first test cylinder 121 is connected to the main hydraulic power unit 200 and the auxiliary hydraulic power unit 300. The main hydraulic power unit 200 or the auxiliary hydraulic power unit 300 supplies pressurized oil to the first test cylinder 121. The pressurized oil enters the first test cylinder 121 and establishes a pressurized oil environment within the sealed cavity. The seals installed inside the first test cylinder 121 form a sealing contact surface under the action of the pressurized oil. The drive end of the first servo electric cylinder 122 is connected to the piston end of the first test cylinder 121. The first servo electric cylinder 122 drives the piston to move within the first test cylinder 121. The reciprocating motion causes the seal to slide with the piston under pressure oil conditions. The pressure established by the oil in the sealing cavity, the reciprocating speed and stroke driven by the first servo electric cylinder 122 are all performed according to the parameters set in GB / T32217-2015 standard. This standard specifies the unified conditions and test methods for seal performance testing, so that the test results only reflect the performance differences of the seal itself and eliminate the influence of actual installation structure differences on the test results. Therefore, the first test fixture 120 can test the sealing performance of the seal itself under standardized conditions.

[0038] The first test cylinder 121 is connected to both the main hydraulic power unit 200 and the auxiliary hydraulic power unit 300, allowing it to obtain pressure oil at both the first and second flow rates from the main hydraulic power unit 200 and the auxiliary hydraulic power unit 300. When the operation of the simulation fixture 110 causes pressure fluctuations in the main hydraulic power unit 200, these fluctuations exist only in the connection pipeline between the main hydraulic power unit 200 and the first test cylinder 121 and are not transmitted to the first test cylinder 121 through the auxiliary hydraulic power unit 300. This ensures that the first test cylinder 121 is not interrupted or experiences measurement deviations due to pressure fluctuations in the main hydraulic power unit 200 during standardized sealing tests. Furthermore, when the main hydraulic power unit 200 stops supplying oil due to maintenance or malfunction, the first test cylinder 121 can switch to the auxiliary hydraulic power unit 300 to continue receiving pressure oil, maintaining the continuous operation of the standardized sealing tests.

[0039] like Figure 5 As shown, the second test fixture 130 includes a second test cylinder 131 and a second servo electric cylinder 132. The second test cylinder 131 is used to install the seal. The drive end of the second servo electric cylinder 132 is connected to the piston end of the second test cylinder 131. The second test cylinder 131 is connected to the main hydraulic power unit 200 and the auxiliary hydraulic power unit 300.

[0040] The second test cylinder 131 is connected to both the main hydraulic power unit 200 and the auxiliary hydraulic power unit 300, allowing it to obtain pressure oil at either the first or second flow rate from the main hydraulic power unit 200. When the simulation fixture 110 causes pressure fluctuations in the main hydraulic power unit 200, these fluctuations exist only in the connection line between the main hydraulic power unit 200 and the second test cylinder 131 and are not transmitted to the second test cylinder 131 through the auxiliary hydraulic power unit 300. This ensures that the second test cylinder 131 is not interrupted or experiences measurement deviations due to pressure fluctuations in the main hydraulic power unit 200 during standardized sealing tests. Furthermore, when the main hydraulic power unit 200 stops supplying oil due to maintenance or malfunction, the second test cylinder 131 can switch to the auxiliary hydraulic power unit 300 to continue receiving pressure oil, maintaining the continuous operation of standardized sealing tests.

[0041] It should be noted that the second test fixture 130 has the same testing principle as the first test fixture 120 mentioned above, and will not be described again here.

[0042] like Figure 1 and Figure 2As shown, the main hydraulic power unit 200 includes a first oil tank 2010, a first oil inlet pipe 2020, a first oil return pipe 2030, a variable displacement piston pump assembly 2040, and a first heat exchanger 2050. One end of the first oil inlet pipe 2020 is connected to the first oil tank 2010 through the variable displacement piston pump assembly 2040, and the other end is connected to the simulation fixture 110 through the servo valve 10, and is also connected to the first test fixture 120 and the second test fixture 130 through the first proportional pressure regulating valve 20. One end of the first oil return pipe 2030 is connected to the first oil tank 2010 through the first heat exchanger 2050, and the other end is connected to the simulation fixture 110 through the servo valve 10, and is also connected to the first test fixture 120 and the second test fixture 130 through the proportional relief valve 30.

[0043] The main hydraulic power unit 200 draws pressurized oil from the first oil tank 2010 through the variable displacement piston pump assembly 2040 and sends it into the first oil inlet pipe 2020. The first oil inlet pipe 2020 supplies oil to the simulation cylinder 111 via the servo valve 10 and to the first test cylinder 121 and the second test cylinder 131 via the first proportional pressure regulating valve 20. The return oil from the simulation cylinder 111 flows through the servo valve 10 and the return oil from the first test cylinder 121 and the second test cylinder 131, and then flows into the first return oil pipe 2 via the proportional relief valve 30. 030, after being cooled by the first heat exchanger 2050, returns to the first oil tank 2010, completing the oil circulation; among them, the variable piston pump group 2040 adjusts the piston stroke length by changing the swashplate tilt angle. When the swashplate tilt angle increases, the piston stroke becomes longer and the volume of oil discharged in a single rotation increases, thereby increasing the total amount of oil output by the pump per unit time. In addition, the piston and cylinder bore have high fitting precision and low volumetric efficiency loss under high pressure, so that the main hydraulic power unit 200 can output pressure oil with the first flow rate.

[0044] The first oil inlet pipe 2020 has three independent oil supply branches connected to the simulation cylinder 111, the first test cylinder 121, and the second test cylinder 131, respectively. Each branch does not affect the others at the oil supply end. The servo valve 10 controls the oil flow rate and direction of the simulation cylinder 111, and the first proportional pressure regulating valve 20 controls the pressure of the oil supplied to the first test cylinder 121 and the second test cylinder 131, respectively, so that each branch can independently adjust according to the oil supply conditions required by the cylinders it is connected to. The return oil is cooled by the first heat exchanger 2050 and then returns to the first oil tank 2010, which reduces the oil temperature when the return oil enters the first oil tank 2010. This avoids the high-temperature oil returning directly to the oil tank, which would cause the oil temperature in the oil tank to rise continuously, thereby reducing the load on the first heat exchanger 2050 to cool the oil in the oil tank.

[0045] It should be noted that the variable displacement piston pump assembly 2040 is existing technology and is not an improvement in this embodiment, so it will not be described in detail here.

[0046] In this preferred embodiment, the first heat exchanger 2050 is a water-cooled heat exchanger.

[0047] In a preferred embodiment, the first oil tank 2010 is further provided with a liquid level sensor, a temperature sensor and a filter; the first oil inlet pipe 2020 is further provided with a filter, a pressure sensor and a temperature sensor; and the first oil return pipe 2030 is further provided with a filter and a temperature sensor.

[0048] like Figure 2 As shown, the main hydraulic power unit 200 also includes a circulation pipe 2060, a circulation pump 2070 and a heater 2080. One end of the circulation pipe 2060 is connected to the first oil tank 2010, and the other end is connected to the first return oil pipe 2030 through the circulation pump 2070 and the heater 2080.

[0049] The circulating pump 2070 draws oil from the first oil tank 2010 and sends it into the circulating pipeline 2060. After being heated by the heater 2080, it is sent to the first return oil pipe 2030 and then back to the first oil tank 2010 via the first return oil pipe 2030. This allows the oil to gradually heat up during the circulation process, avoiding the problem of localized excessively high oil temperatures caused by the heater 2080 heating the oil inside the tank while the oil temperature in other areas remains below the required operating temperature. The heating process occurs before the oil supply process when the system starts up. After the oil circulates multiple times through the circulating pipeline 2060, the oil temperature in each area of ​​the first oil tank 2010 gradually becomes uniform. Then, the variable displacement piston pump group 2040 supplies oil to each cylinder. This avoids the problem of increased oil supply pipeline resistance due to excessive oil viscosity and insufficient deformation of the seals at low temperatures when the low-temperature oil directly enters the simulation cylinder 111, the first test cylinder 121, and the second test cylinder 131, which would affect the sealing test results. like Figure 2 As shown, the main hydraulic power unit 200 also includes a first emergency pipe 2090 and a first electromagnetic unloading valve 2100. The first emergency pipe 2090 is connected to the first oil inlet pipe 2020 and the first oil return pipe 2030 through the first electromagnetic unloading valve 2100.

[0050] Under normal oil supply conditions, the first electromagnetic unloading valve 2100 is closed, preventing the connection between the first oil inlet pipe 2020 and the first oil return pipe 2030. All the pressure oil output by the variable piston pump group 2040 enters each cylinder for driving the sealing test through the first oil inlet pipe 2020. When the variable piston pump group 2040 stops working or the system needs to be unloaded quickly, the first electromagnetic unloading valve 2100 opens, connecting the first oil inlet pipe 2020 to the first oil return pipe 2030 through the first emergency pipe 2090. The residual pressure oil in the first oil inlet pipe 2020 returns to the first oil tank 2010 through the first emergency pipe 2090 and the first oil return pipe 2030.

[0051] like Figure 2 As shown, the main hydraulic power unit 200 also includes a first accumulator 2110, which is connected to the first oil inlet pipe 2020.

[0052] The first accumulator 2110 is connected to the first oil inlet pipe 2020, allowing it to store a portion of pressurized oil during the process of the variable piston pump assembly 2040 outputting pressurized oil to the first oil inlet pipe 2020. When the simulated cylinder 111 undergoes high-frequency reciprocating motion, causing the instantaneous oil supply demand to exceed the maximum output of the variable piston pump assembly 2040 per unit time, the first accumulator 2110 releases the stored pressurized oil to the first oil inlet pipe 2020 to supplement the insufficient output of the variable piston pump assembly 2040. This prevents the simulated cylinder 111 from experiencing a decrease in movement speed due to insufficient oil supply, thereby ensuring the sealing test process. The reciprocating speed of the central seal is consistent with the set value; when the servo valve 10 closes or reverses, causing the pressure in the first oil inlet pipe 2020 to rise instantaneously, the first accumulator 2110 absorbs the excess pressure oil in the oil inlet pipe, reduces the pressure peak in the first oil inlet pipe 2020, and avoids leakage of the pipeline joint or damage to the pressure sensor due to excessive instantaneous pressure in the first oil inlet pipe 2020; the pressure oil output by the variable piston pump group 2040 has pressure pulsation, and the first accumulator 2110 absorbs the pressure pulsation through the process of storing and releasing pressure oil, thereby reducing the pressure fluctuation amplitude in the first oil inlet pipe 2020.

[0053] like Figure 2 As shown, the first oil inlet pipe 2020 has several first spare interfaces 2120. The first spare interfaces 2120 are used to connect to new oil supply branches without modifying the first oil inlet pipe 2020, and to connect to other oil tanks in extreme cases to ensure sufficient oil supply.

[0054] like Figure 2 As shown, the first oil inlet pipe 2020 has a first sampling port 2130. The first sampling port 2130 is used to collect oil samples from the first oil inlet pipe 2020 without disassembling the pipeline, so as to detect the oil contamination level during system operation.

[0055] like Figure 2 As shown, the first return oil pipe 2030 has several second spare interfaces 2140. The second spare interfaces 2140 are used to connect to new return oil branches without modifying the first return oil pipe 2030, and in extreme cases, to connect to other oil tanks to discharge the hydraulic oil in the first return oil pipe 2030.

[0056] like Figure 1 and Figure 3As shown, the auxiliary hydraulic power unit 300 includes a second oil tank 3010, a second oil inlet pipe 3020, a second oil return pipe 3030, a fixed displacement piston pump assembly 3040, and a second heat exchanger 3050. One end of the second oil inlet pipe 3020 is connected to the second oil tank 3010 via the fixed displacement piston pump assembly 3040, and the other end is connected to the first test fixture 120 and the second test fixture 130 via the first proportional pressure regulating valve 20. One end of the second oil return pipe 3030 is connected to the second oil tank 3010 via the second heat exchanger 3050, and the other end is connected to the first test fixture 120 and the second test fixture 130 via the proportional relief valve 30.

[0057] The fixed displacement plunger pump assembly 3040 draws pressurized oil from the second oil tank 3010 and sends it into the second inlet pipe 3020. The oil is then supplied to the first test fixture 120 and the second test fixture 130 via the first proportional pressure regulating valve 20. The return oil from the first test fixture 120 and the second test fixture 130 flows into the second return oil pipe 3030 via the proportional relief valve 30. After being cooled by the second heat exchanger 3050, the oil returns to the second oil tank 3010. The output flow rate of the fixed displacement plunger pump assembly 3040 is constant and does not change with the load pressure. The first proportional pressure regulating valve 20 controls the oil pressure supplied to the first test fixture 120 and the second test fixture 130 by adjusting the bypass relief flow rate.

[0058] The fixed displacement plunger pump group 3040 has a constant output flow rate that is less than the first output flow rate of the variable displacement plunger pump group 2040. This matches the characteristics of the first test fixture 120 and the second test fixture 130, which only need to establish a pressure oil environment in the sealed cavity and have no rigid requirement for the oil supply flow rate. This avoids the energy waste caused by a large amount of pressure oil overflowing back to the oil tank through the proportional relief valve 30 when using the variable displacement plunger pump group 2040, due to the output flow rate being much greater than the actual demand. The constant output flow rate of the fixed displacement plunger pump group 3040 ensures that the bypass overflow flow rate of the first proportional pressure regulating valve 20 is not affected by the flow fluctuation at the oil supply end when adjusting the oil pressure supplied to the first test fixture 120 and the second test fixture 130, making the pressure regulation process more stable. The first test fixture 120 and the second test fixture 130... Fixture 130 is connected to both the main hydraulic power unit 200 and the auxiliary hydraulic power unit 300. The fixed displacement piston pump group 3040 of the auxiliary hydraulic power unit 300 outputs a second flow rate, and the variable displacement piston pump group 2040 of the main hydraulic power unit 200 outputs a first flow rate. Both supply oil to the first test fixture 120 and the second test fixture 130 independently. When the pressure of the main hydraulic power unit 200 fluctuates due to the operation of the simulation fixture 110, the fluctuation only exists in the oil supply line of the main hydraulic power unit 200 and will not be transmitted to the first test fixture 120 and the second test fixture 130 through the auxiliary hydraulic power unit 300. This avoids interference of the operating conditions of the simulation fixture 110 on the sealing test of the first test fixture 120 and the second test fixture 130.

[0059] It should be noted that the quantitative plunger pump assembly 3040 is existing technology and is not an improvement in this embodiment, so it will not be described in detail here.

[0060] In this preferred embodiment, the second heat exchanger 3050 is a water-cooled heat exchanger.

[0061] In a preferred embodiment, the second oil tank 3010 is further provided with a liquid level sensor, a temperature sensor and a filter; the second oil inlet pipe 3020 is further provided with a filter, a pressure sensor and a temperature sensor; and the second oil return pipe 3030 is further provided with a filter and a temperature sensor.

[0062] like Figure 3 As shown, the second oil inlet pipe 3020 has several third spare interfaces 3060. The third spare interfaces 3060 are used to connect to new oil supply branches without modifying the second oil inlet pipe 3020, and to connect to other oil tanks in extreme cases to ensure sufficient oil supply.

[0063] like Figure 3 As shown, the second return oil pipe 3030 has several fourth spare interfaces 3070. The fourth spare interfaces 3070 are used to connect to new return oil branches without modifying the second return oil pipe 3030, and in extreme cases, to connect to other oil tanks to discharge the hydraulic oil in the first return oil pipe 2030.

[0064] like Figure 3 As shown, the second oil inlet pipe 3020 has a second sampling port 3080. The second sampling port 3080 is used to collect oil samples from the second oil inlet pipe 3020 without disassembling the pipeline, so as to detect the oil contamination level during system operation.

[0065] like Figure 3 As shown, the auxiliary hydraulic power unit 300 also includes a second emergency pipe 3090 and a second electromagnetic unloading valve 3100. The second emergency pipe 3090 is connected to the second oil inlet pipe 3020 and the second oil return pipe 3030 through the second electromagnetic unloading valve 3100.

[0066] Under normal oil supply conditions, the second electromagnetic unloading valve 3100 is closed, preventing the second oil inlet pipe 3020 from connecting with the second oil return pipe 3030. All the pressure oil output by the quantitative plunger pump group 3040 enters the first test fixture 120 and the second test fixture 130 through the second oil inlet pipe 3020 to perform sealing tests. When the system needs to be unloaded quickly, the second electromagnetic unloading valve 3100 is opened, connecting the second oil inlet pipe 3020 with the second oil return pipe 3030 through the second emergency pipe 3090. The residual pressure oil in the second oil inlet pipe 3020 returns to the second oil tank 3010 through the second emergency pipe 3090 and the second oil return pipe 3030, causing the pressure in the second oil inlet pipe 3020 to drop to near zero in a short time, preventing the pressure oil from being trapped in the oil inlet pipe for a long time, which could lead to pipeline leakage or deformation of the seals due to pressure.

[0067] like Figure 3 As shown, the auxiliary hydraulic power unit 300 also includes a second accumulator 3110, which is connected to the second oil inlet pipe 3020.

[0068] The second accumulator 3110 is connected to the second oil inlet pipe 3020, allowing it to store a portion of the pressurized oil during the process of the metering plunger pump assembly 3040 outputting pressurized oil to the second oil inlet pipe 3020. When a momentary leak occurs in the seal of the first test fixture 120 or the second test fixture 130 during the test, causing a momentary drop in pressure within the second oil inlet pipe 3020, the second accumulator 3110 releases the stored pressurized oil into the second oil inlet pipe 3020 to replenish the momentary pressure loss caused by the leak, restoring the pressure within the second oil inlet pipe 3020 to the set value and preventing the first test fixture 120 or the second test fixture 130 from experiencing pressure loss due to oil supply issues. Pressure drop causes the sealing test conditions to deviate from the set value; when the oil circuit switching of either the first test fixture 120 or the second test fixture 130 causes the pressure in the second oil inlet pipe 3020 to rise instantaneously, the second accumulator 3110 absorbs the excess pressurized oil in the oil inlet pipe, reduces the pressure peak in the second oil inlet pipe 3020, and avoids leakage of the pipeline joint or damage to the pressure sensor due to excessive instantaneous pressure in the second oil inlet pipe 3020; the pressure oil output by the quantitative plunger pump group 3040 has pressure pulsation, and the second accumulator 3110 absorbs the pressure pulsation through the process of storing and releasing pressure oil, thereby reducing the pressure fluctuation amplitude in the second oil inlet pipe 3020.

[0069] like Figure 3 As shown, the auxiliary hydraulic power unit 300 also includes a third emergency pipe 3120 and a second proportional pressure regulating valve 3130. The third emergency pipe 3120 is connected to the second emergency pipe 3090 and the second oil inlet pipe 3020 through the second proportional pressure regulating valve 3130.

[0070] Under normal oil supply conditions, the second electromagnetic unloading valve 3100 is closed, the third emergency pipe 3120 is not connected to the second return oil pipe 3030, and the second proportional pressure regulating valve 3130 does not participate in the oil supply process. When the output pressure of the quantitative plunger pump group 3040 exceeds the oil supply pressure required by the first test fixture 120 and the second test fixture 130, the second proportional pressure regulating valve 3130 opens, allowing part of the pressurized oil in the second inlet pipe 3020 to flow into the second return oil pipe 3030 and return to the second oil tank 3010 through the third emergency pipe 3120, the second emergency pipe 3090, and the second electromagnetic unloading valve 3100. The amount of oil leakage is controlled by adjusting the opening of the second proportional pressure regulating valve 3130, allowing the second inlet pipe 3020 to flow into the second return oil pipe 3030 and return to the second oil tank 3010. The oil supply pressure in the oil pipe 3020 is stabilized at the set value, which avoids the output pressure of the fixed displacement plunger pump group 3040 being too high, causing the seals in the first test fixture 120 and the second test fixture 130 to bear oil pressure exceeding the test requirements and affecting the test results; when the second electromagnetic unloading valve 3100 fails to open due to a malfunction, the second proportional pressure regulating valve 3130 can release the pressure oil in the second oil inlet pipe 3020 into the second oil return pipe 3030 through the third emergency pipe 3120 and the second emergency pipe 3090, so that the pressure in the second oil inlet pipe 3020 drops, avoiding the second oil inlet pipe 3020 from being unable to depressurize when the second electromagnetic unloading valve 3100 fails, which would cause the pipeline to be pressurized for a long time.

[0071] Specifically, the capacity of the first oil tank 2010 is greater than that of the second oil tank 3010. The first oil tank 2010 provides sufficient oil storage for the variable displacement piston pump assembly 2040 to supply pressurized oil at the first flow rate to the simulated cylinder 111 from the first inlet pipe 2020. When the simulated cylinder 111 experiences a sudden surge in oil return to the first oil tank 2010 due to high-frequency reciprocating motion, the oil level in the first oil tank 2010 remains above the minimum suction level, preventing a sudden rise in the oil level and overflow. Simultaneously, when the variable displacement piston pump assembly 2040 draws oil from the first oil tank 2010, the oil level in the first oil tank 2010 is never lower than the height of the suction pipe opening, preventing air from being drawn into the suction pipe and causing the variable displacement piston pump assembly 2040 to cavitate. The larger capacity of the first oil tank 2010 ensures that the variable displacement piston pump assembly 2040 can operate smoothly during the initial startup phase. When oil is drawn from the first oil tank 2010, the oil will not be quickly emptied due to the small oil volume. When the variable piston pump set 2040 is running continuously, the oil temperature in the first oil tank 2010 rises slowly due to the volume effect, avoiding the oil temperature from rising too quickly due to multiple cycles in a short period of time. The capacity of the second oil tank 3010 is smaller than that of the first oil tank 2010. The second oil tank 3010 only needs to supply the second flow rate to the first test fixture 120 and the second test fixture 130. The second test fixture 130 and the first test fixture 120 have no rigid requirements for the oil supply flow rate. Their return oil volume is much smaller than that of the simulated cylinder 111. The smaller capacity of the second oil tank 3010 is sufficient to meet the oil supply requirements, and it occupies less space.

[0072] It should be noted that, in this document, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Unless otherwise specified, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes that element.

[0073] Furthermore, it should be noted that the scope of the methods and apparatus in the embodiments of this application is not limited to performing functions in the order shown or discussed, but may also include performing functions substantially simultaneously or in the reverse order, depending on the functions involved. For example, the described methods may be performed in a different order than described, and various steps may be added, omitted, or combined. In addition, features described with reference to certain examples may be combined in other examples.

[0074] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any changes or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in the present invention should be included within the scope of protection of the present invention.

Claims

1. A high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system, characterized in that, include: Multiple testing devices are used to install the seals and perform sealing tests on them. A main hydraulic power unit, connected to multiple of the test devices, is used to supply pressurized oil with a first flow rate to the test devices per unit time; A secondary hydraulic power unit, connected to multiple of the aforementioned test devices, is used to supply pressurized oil with a second flow rate to the test devices per unit time; Wherein, the first flow rate is greater than the second flow rate.

2. The high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system according to claim 1, characterized in that, At least one of the test devices includes a simulation fixture and a first test fixture, wherein the simulation fixture is used to test the sealing reliability of the seal under simulated real installation conditions, and the first test fixture is used to test the sealing performance of the seal itself under standardized conditions. The main hydraulic power unit is connected to the simulation fixture and the first test fixture, and the auxiliary hydraulic power unit is connected to the first test fixture.

3. The high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system according to claim 2, characterized in that, At least one of the testing devices includes a second test fixture for testing the sealing performance of the seal itself under standardized conditions; The main hydraulic power unit is connected to the second test fixture, and the auxiliary hydraulic power unit is also connected to the second test fixture.

4. The high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system according to claim 3, characterized in that, The simulation fixture includes a simulation cylinder and a load spring. The simulation cylinder is used to install seals, and the load spring is installed on the piston end of the simulation cylinder. The simulation cylinder is connected to the main hydraulic power unit. And / or, the first test fixture includes a first test cylinder and a first servo electric cylinder, the first test cylinder is used to install the seal, the drive end of the first servo electric cylinder is connected to the piston end of the first test cylinder, and the first test cylinder is connected to the main hydraulic power device and the auxiliary hydraulic power device; And / or, the second test fixture includes a second test cylinder and a second servo electric cylinder, the second test cylinder is used to install the seal, the drive end of the second servo electric cylinder is connected to the piston end of the second test cylinder, and the second test cylinder is connected to the main hydraulic power device and the auxiliary hydraulic power device.

5. The high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system according to claim 3, characterized in that, The main hydraulic power unit includes a first oil tank, a first oil inlet pipe, a first oil return pipe, a variable displacement piston pump assembly, and a first heat exchanger. One end of the first oil inlet pipe is connected to the first oil tank through the variable displacement piston pump assembly, and the other end is connected to the simulation fixture through a servo valve. It is also connected to the first test fixture and the second test fixture through a first proportional pressure regulating valve. One end of the first return oil pipe is connected to the first oil tank through the first heat exchanger, and the other end is connected to the simulation fixture through the servo valve, and is also connected to the first test fixture and the second test fixture through the proportional overflow valve.

6. The high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system according to claim 5, characterized in that, The main hydraulic power unit also includes a circulation pipeline, a circulation pump and a heater. One end of the circulation pipeline is connected to the first oil tank, and the other end is connected to the first return oil pipe through the circulation pump and the heater. And / or, the main hydraulic power unit further includes a first emergency pipe and a first electromagnetic unloading valve, wherein the first emergency pipe is connected to the first oil inlet pipe and the first oil return pipe through the first electromagnetic unloading valve; And / or, the main hydraulic power unit further includes a first accumulator, which is connected to the first oil inlet pipe.

7. The high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system according to claim 5, characterized in that, The first oil inlet pipe has several first spare interfaces; And / or, the first oil inlet pipe has a first sampling port; And / or, the first return line has several second spare interfaces.

8. The high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system according to claim 5, characterized in that, The auxiliary hydraulic power unit includes a second oil tank, a second oil inlet pipe, a second oil return pipe, a fixed displacement piston pump assembly, and a second heat exchanger; one end of the second oil inlet pipe is connected to the second oil tank through the fixed displacement piston pump assembly, and the other end is connected to the first test fixture and the second test fixture through a first proportional pressure regulating valve; One end of the second return oil pipe is connected to the second oil tank through the second heat exchanger, and the other end is connected to the first test fixture and the second test fixture through a proportional overflow valve.

9. A high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system according to claim 8, characterized in that, The second oil inlet pipe has several third spare interfaces; And / or, the second return line has several fourth spare interfaces; And / or, the second oil inlet pipe has a second sampling port; And / or, the auxiliary hydraulic power unit further includes a second emergency pipe and a second electromagnetic unloading valve, wherein the second emergency pipe is connected to the second oil inlet pipe and the second oil return pipe through the second electromagnetic unloading valve; And / or, the auxiliary hydraulic power unit further includes a second accumulator, which is connected to the second oil inlet pipe.

10. A high-pressure multi-channel multi-field coupled reciprocating dynamic seal integrated test system according to claim 9, characterized in that, The auxiliary hydraulic power unit also includes a third emergency pipe and a second proportional pressure regulating valve, wherein the third emergency pipe is connected to the second emergency pipe and the second oil inlet pipe through the second proportional pressure regulating valve; And / or, the capacity of the first fuel tank is greater than the capacity of the second fuel tank.

Images