Hydraulic systems, high-pressure, high-flow-rate inertial load hydraulic test bench and methods

Abstract

This invention discloses a hydraulic system and a high-pressure, high-flow-rate inertial load hydraulic test bench and method. The hydraulic system includes: a loading cylinder, comprising a first bidirectional hydraulic cylinder and a second bidirectional hydraulic cylinder; a directional valve connected to the loading cylinder, comprising a first directional valve and a second directional valve; a first inertial loading guide hydraulic cylinder; a second inertial loading guide hydraulic cylinder; a first inertial loading motor connected between two ports of the first inertial loading guide hydraulic cylinder; a second inertial loading motor connected between two ports of the second inertial loading guide hydraulic cylinder; and multiple switching valves for switching the connection relationship between the loading cylinder and the directional valves, and under the action of the directional valves, enabling the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder to achieve bypass working mode, series working mode, and parallel working mode.

Description

Technical Field

[0001] This invention relates to the field of high-pressure, high-flow hydraulic systems and inertial load testing technology, and particularly to hydraulic systems, high-pressure, high-flow inertial load hydraulic test benches and methods. Background Technology

[0002] With the rise of marine engineering, more and more ships and underwater equipment are equipped with large inertial loads. Test benches, while simulating loads, also need to handle large inertial loads. Most existing hydraulic loading test benches can only simulate the load of a single actuator through pressure and flow regulation, failing to meet the requirements for high-pressure, high-flow-rate inertial load hydraulic simulation experiments. Current technologies generally use mechanical inertia for inertial loading, directly connecting a flywheel or mass block to the load. This method has poor safety and is inconvenient to adjust. Some existing technologies use electrical inertia, employing a loading motor to achieve inertial loading, but this cannot meet the requirements for simulating inertial loads in high-pressure, high-flow-rate hydraulic systems. While some existing hydraulic test benches use hydraulic methods and hydraulic motors for inertial loading, the inertial loading is located after the load and can only be used for rotating loads, unable to simulate moving loads in hydraulic cylinders. The inertial simulation suffers from poor time-domain matching and substitutability, failing to simulate and reproduce real inertial forces, and thus cannot meet the requirements for high-pressure, high-flow-rate inertial load hydraulic simulation experiments. Summary of the Invention

[0003] In view of the above-mentioned defects or improvement needs of the existing technology, the present invention provides a hydraulic system and a high-pressure, high-flow-rate inertial load hydraulic test bench, which can realize multiple mode switching and meet the needs of various high-pressure, high-flow-rate inertial load hydraulic simulation experiments.

[0004] To achieve the above objectives, the present invention adopts the following technical solution.

[0005] In some embodiments, a hydraulic system is provided, the hydraulic system comprising:

[0006] The loading cylinder includes a first bidirectional hydraulic cylinder and a second bidirectional hydraulic cylinder;

[0007] A reversing valve, connected to the loading cylinder, includes a first reversing valve and a second reversing valve;

[0008] First inertia loading guide hydraulic cylinder;

[0009] Second inertial loading guide hydraulic cylinder;

[0010] A first inertial loading motor is connected between the first oil port and the second oil port of the first inertial loading guide hydraulic cylinder.

[0011] The second inertial loading motor is connected between the first oil port and the second oil port of the second inertial loading guide hydraulic cylinder.

[0012] Multiple switching valves are used to switch the connection between the loading cylinder and the directional valve, and under the action of the directional valve, the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder can achieve bypass working mode, series working mode, and parallel working mode.

[0013] In some embodiments, the switching valve includes a first switching valve, a second switching valve, and a third switching valve, wherein the first switching valve is connected between the first oil port of the first bidirectional hydraulic cylinder and the first interface of the first directional valve, the second switching valve is connected between the first oil port of the second bidirectional hydraulic cylinder and the second interface of the first directional valve, and the third switching valve is connected between the second oil port of the first bidirectional hydraulic cylinder and the second oil port of the second bidirectional hydraulic cylinder.

[0014] In some embodiments, the switching valve includes a fourth switching valve, a fifth switching valve, and a sixth switching valve, wherein the fourth switching valve is connected between the second oil port of the first bidirectional hydraulic cylinder and the second interface of the first directional valve, the fifth switching valve is connected between the first oil port of the second bidirectional hydraulic cylinder and the first interface of the second directional valve, and the sixth switching valve is connected between the second oil port of the second bidirectional hydraulic cylinder and the second interface of the second directional valve.

[0015] In some embodiments, the switching valve includes a seventh switching valve, an eighth switching valve, a ninth switching valve, and a tenth switching valve, wherein the seventh switching valve is connected between the first oil port and the second oil port of the first bidirectional hydraulic cylinder, the eighth switching valve is connected between the first oil port and the second oil port of the second bidirectional hydraulic cylinder, the ninth switching valve is connected between the first oil port and the second oil port of the first inertial loading guide hydraulic cylinder, and the tenth switching valve is connected between the first oil port and the second oil port of the second inertial loading guide hydraulic cylinder.

[0016] In some embodiments, the plurality of switching valves are all ball valves, and the ball valves are electrically controlled switching valves.

[0017] In some embodiments, both the first directional valve and the second directional valve are three-position four-way solenoid directional valves, and both the first directional valve and the second directional valve are servo directional valves.

[0018] In some embodiments, the first inertial loading motor and the second inertial loading motor are bidirectional vane pumps.

[0019] In some embodiments, two pilot-operated electrically controlled relief valves in opposite directions are connected in parallel between the first oil port and the second oil port of the first bidirectional hydraulic cylinder.

[0020] The second bidirectional hydraulic cylinder has two pilot-operated electrically controlled relief valves connected in parallel between its first and second oil ports.

[0021] In some embodiments, the hydraulic system further includes multiple pressure sensors and multiple check valves. Each oil port of the first bidirectional hydraulic cylinder, the second bidirectional hydraulic cylinder, the first inertial loading guide hydraulic cylinder, and the second inertial loading guide hydraulic cylinder is connected to a pressure sensor, and a check valve is provided between each pressure sensor and its corresponding oil port.

[0022] In some embodiments, a high-pressure, high-flow-rate inertial load hydraulic test bench is also provided, the high-pressure, high-flow-rate inertial load hydraulic test bench comprising a hydraulic system according to any of the preceding embodiments.

[0023] Compared to existing technologies, the beneficial effects of this invention are at least as follows: In the embodiments of this application, two directional valves and multiple switching valves are used to switch between parallel and series operation modes of the two loading cylinders to meet different loading requirements. In the embodiments of this application, the two inertial loading guide hydraulic cylinders simulate different inertial forces through an inertial loading motor and a switching valve, respectively. By adjusting the inertial load mass of the inertial loading motor, the inertial load of the inertial loading guide hydraulic cylinder can be quickly adjusted and simulated, thereby enabling the inertial loading guide hydraulic cylinder to simulate different inertial forces. Through the controllable adjustment of the loads of the two loading cylinders and the two inertial loading guide hydraulic cylinders, the entire hydraulic system can simulate high-pressure, high-flow-rate inertial load hydraulic tests. In the embodiments of this application, the moving inertial load is replaced by a rotating inertial load. By setting the inertial loading motor and the inertial loading guide hydraulic cylinder, it is converted into a moving load, decoupling the inertial load itself from the inertial loading guide hydraulic cylinder. The rotating inertial load mass can be directly replaced, conveniently simulating the load inertial forces experienced by various moving hydraulic cylinders, with high safety. Furthermore, by decoupling the setup, the problem of difficult-to-control guidance of moving loads can be avoided, and errors caused by friction during the guidance of moving loads can also be reduced.

[0024] It is understood that the description of the beneficial effects in this application is merely a direct representation of the beneficial effects in some embodiments of this application, and the effects of other technical solutions and features of this application can be referred to the relevant descriptions in the specific embodiments. Furthermore, the fact that the specification does not mention the technical effects of the relevant solutions in detail should not negate the fact that the technical effects of the relevant solutions in this application are essentially unambiguous. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the overall structure of a hydraulic system according to an embodiment of the present invention.

[0026] Figure 2This is a schematic diagram of the overall structure of a hydraulic system in a series working mode according to an embodiment of the present invention.

[0027] Figure 3 This is a schematic diagram of the overall structure of a hydraulic system in parallel operation mode according to an embodiment of the present invention.

[0028] Figure 4 This is a schematic diagram of the overall structure of a hydraulic system in bypass working mode according to an embodiment of the present invention.

[0029] Figure 5 This is a schematic diagram of the overall structure of a high-pressure, high-flow-rate inertial load hydraulic test bench according to an embodiment of the present invention.

[0030] Figure 6 This is a schematic diagram of the structure of a high-pressure, high-flow-rate inertial load hydraulic test bench according to an embodiment of the present invention.

[0031] Figure 7 This is a schematic diagram of the structure of a high-pressure, high-flow-rate inertial load hydraulic test bench according to an embodiment of the present invention.

[0032] Figure 8 This is a partial structural diagram of a hydraulic system in a series working mode according to an embodiment of the present invention.

[0033] Figure 9 This is a partial structural diagram of a hydraulic system in parallel operation mode according to an embodiment of the present invention.

[0034] Figure 10 This is a partial structural diagram of a hydraulic system in bypass operating mode according to an embodiment of the present invention. Detailed Implementation

[0035] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention.

[0036] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0037] In some embodiments of this application, a hydraulic system is provided, the hydraulic system comprising: a loading cylinder, including a first bidirectional hydraulic cylinder 101 and a second bidirectional hydraulic cylinder 102;

[0038] A reversing valve, connected to the loading cylinder, includes a first reversing valve 201 and a second reversing valve 202;

[0039] First inertial loading guide hydraulic cylinder 301;

[0040] Second inertial loading guide hydraulic cylinder 302;

[0041] The first inertial loading motor 401 is connected between the first oil port and the second oil port of the first inertial loading guide hydraulic cylinder 301.

[0042] The second inertial loading motor 402 is connected between the first oil port and the second oil port of the second inertial loading guide hydraulic cylinder 302.

[0043] Multiple switching valves are used to switch the connection relationship between the loading cylinder and the reversing valve, and under the action of the reversing valve, the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 can achieve bypass working mode, series working mode and parallel working mode.

[0044] In the embodiments of this application, one of the two oil ports of the first inertial loading guide hydraulic cylinder 301 is a first oil port and the other is a second oil port. Similarly, one of the two oil ports of the second inertial loading guide hydraulic cylinder 302 is a first oil port and the other is a second oil port. Both the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 also include a first oil port and a second oil port. Figure 1As shown in the specific embodiment of this application, port A of the first inertial loading guide hydraulic cylinder 301 is the first port, and port B is the second port. Port A of the second inertial loading guide hydraulic cylinder 302 is the first port, and port B is the second port. Port A of the first bidirectional hydraulic cylinder 101 is the first port, and port B is the second port. Port A of the second bidirectional hydraulic cylinder is the first port, and port B is the second port. By combining and controlling two directional valves and multiple switching valves, the working mode switching of the two loading cylinders working in parallel or in series can be realized to achieve the regulation of various types of loading requirements and to simulate various different load conditions. The two inertial loading guide hydraulic cylinders are respectively controlled by an inertial loading motor and a switching valve to simulate different inertial forces. The inertial loading motor can be adjusted to achieve rapid regulation of the load of the inertial loading guide hydraulic cylinder, so that the inertial loading guide hydraulic cylinder can simulate different inertial forces. Through the controllable adjustment of the loads of the two loading cylinders and the two inertial loading guide hydraulic cylinders, the entire hydraulic system can realize the simulation of high-pressure, high-flow inertial load hydraulic tests.

[0045] In some embodiments, the switching valve includes a first switching valve 501, a second switching valve 502, and a third switching valve 503, wherein the first switching valve 501 is connected between the first oil port of the first bidirectional hydraulic cylinder 101 and the first interface of the first directional valve 201, the second switching valve 502 is connected between the first oil port of the second bidirectional hydraulic cylinder 102 and the second interface of the first directional valve 201, and the third switching valve 503 is connected between the second oil port of the first bidirectional hydraulic cylinder 101 and the second oil port of the second bidirectional hydraulic cylinder 102.

[0046] In some embodiments, both the first reversing valve 201 and the second reversing valve 202 include a first interface and a second interface, which are the working ports of the reversing valves. In embodiments of this application, such as... Figure 1 As shown, port A of the first directional valve 201 is the first interface, and port B is the second interface. Port A of the second directional valve 202 is the first interface, and port B is the second interface. By connecting the first switching valve 501, the second switching valve 502, and the third switching valve 503, the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 can be loaded in series.

[0047] In some embodiments, such as Figure 2 As shown, the first switching valve 501, the second switching valve 502, and the third switching valve 503 are all in the connected position, while the other switching valves are in the closed position, realizing the series loading of the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102. The first inertial loading motor 401 and the second inertial loading motor 402 can realize the passive inertial force loading of the first inertial loading guide hydraulic cylinder 301 and the second inertial loading guide hydraulic cylinder 302, simulating inertial force.

[0048] In the embodiments of this application, in the series loading mode of the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102, the two piston rods of the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 can be connected to the same drive system to simulate the same load, achieve double load simulation under the same hydraulic oil source, and maintain synchronization between the two cylinders. In some embodiments, the simulated load can be a ship hatch cover. In some embodiments, the first inertial loading motor 401 and the second inertial loading motor 402 are connected to an inertial wheel of the same mass as the simulated load. The inertial wheel is connected to the shaft of the first inertial loading motor 401 and the second inertial loading motor 402.

[0049] like Figure 2 As shown, in some embodiments, the hydraulic system includes a main pressure oil pipe and a return oil pipe. In some embodiments, the main pressure oil pipe includes a main pressure oil pipe section P, and the return oil pipe includes a main return oil pipe section T. The main pressure oil pipe section is connected to a hydraulic pump station and is used to transmit stable hydraulic oil at a preset pressure supplied by the hydraulic pump station to the hydraulic system. The main return oil pipe section is connected to an oil tank and is used to recover hydraulic oil. Various hydraulic components can be arranged between the main pressure oil pipe section and the main return oil pipe section to form a complete hydraulic circuit.

[0050] like Figure 8 As shown, in some embodiments, the main pressure oil pipe includes a first directional valve section 3001, a first switching valve section 3002, a first bidirectional hydraulic cylinder A section 3003, a first bidirectional hydraulic cylinder B section 3004, a second bidirectional hydraulic cylinder B section 3005, a second bidirectional hydraulic cylinder A section 3006, a second switching valve section 3007, a second switching valve section 3008, a first directional valve section 3009, and a first directional valve section 3010.

[0051] The first directional valve pipe section 1, the first switch valve pipe section, the first bidirectional hydraulic cylinder A pipe section, the first bidirectional hydraulic cylinder B pipe section, the second bidirectional hydraulic cylinder B pipe section, the second bidirectional hydraulic cylinder A pipe section, the second switch valve pipe section 1, the second switch valve pipe section 2, the first directional valve pipe section 2, and the first directional valve pipe section 3 are connected sequentially. The first directional valve pipe section 1 is directly connected to the main pressure oil pipe section, and the first directional valve pipe section 3 is directly connected to the main return oil pipe section.

[0052] like Figure 2 and Figure 8As shown, in some embodiments, the first directional valve 201 has ports A, B, P, and T. Port P is the inlet port, port T is the return port, and ports A and B are working ports. Ports A, B, P, and T of the first directional valve 201 are respectively connected to the first switching valve section, the second first directional valve section, the first directional valve section one, and the third first directional valve section. One end of the third first directional valve section is connected to port T of the first directional valve, and the other end is connected to the main return oil section.

[0053] In some embodiments, one end of the first directional valve pipe section is connected to the main pressure oil pipe section, the other end of the first directional valve pipe section is connected to the oil port P of the first directional valve 201, one end of the first switching valve pipe section is connected to the first switching valve 501, and the other end of the first switching valve pipe section is connected to the oil port A of the first directional valve 201.

[0054] In some embodiments, the first bidirectional hydraulic cylinder 101 has a chamber A and a chamber B, with chamber A having a first oil port and chamber B having a second oil port. One end of the A section of the first bidirectional hydraulic cylinder is connected to the first switching valve 501, and the other end of the A section of the first bidirectional hydraulic cylinder is connected to the first oil port of the A chamber of the first bidirectional hydraulic cylinder 101.

[0055] In some embodiments, the second bidirectional hydraulic cylinder 102 has a chamber A and a chamber B, with chamber A having a first oil port and chamber B having a second oil port. A third switching valve 503 is provided between the first bidirectional hydraulic cylinder B section and the second bidirectional hydraulic cylinder B section. One end of the first bidirectional hydraulic cylinder B section is connected to the second oil port of the first bidirectional hydraulic cylinder 101's chamber B, and the other end of the first bidirectional hydraulic cylinder B section is connected to the third switching valve 503. One end of the second bidirectional hydraulic cylinder B section is connected to the second oil port of the second bidirectional hydraulic cylinder 102's chamber B, and the other end of the second bidirectional hydraulic cylinder B section is connected to the third switching valve 503.

[0056] In some embodiments, one end of the second bidirectional hydraulic cylinder A pipe section is connected to the first oil port of the A chamber of the second bidirectional hydraulic cylinder 102, the other end of the second bidirectional hydraulic cylinder A pipe section is connected to one end of the second switching valve pipe section one, the other end of the second switching valve pipe section one is connected to the second switching valve 502, one end of the second switching valve pipe section two is connected to the second switching valve 502, and the other end of the second switching valve pipe section two is connected to the first reversing valve pipe section two.

[0057] In the embodiments of this application, the first switching valve 501 is the only switching valve connecting chamber A of the first bidirectional hydraulic cylinder 101 and port A of the first directional valve 201. The first bidirectional hydraulic cylinder 101 is connected to the first directional valve 201 and can serve as a master control switch. In the series operation mode, the first directional valve 201 controls the direction of hydraulic oil in the entire hydraulic circuit. The second switching valve 502 connects the first port of the second bidirectional hydraulic cylinder 102 and port B of the first directional valve 201. The third switching valve 503 connects the second port of the first bidirectional hydraulic cylinder 101 and the second port of the second bidirectional hydraulic cylinder 102, so that when the first switching valve 501, the second switching valve 502, and the third switching valve 503 are simultaneously connected, the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 are connected in series between the main pressure oil pipe and the main return oil pipe, and the first directional valve 201 can simultaneously control the series-connected first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102. In the series mode, the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 have the same loading capacity and have the characteristic of natural loading synchronization, which can achieve double loading on the simulated load object.

[0058] In some embodiments, the switching valve includes a fourth switching valve 504, a fifth switching valve 505, and a sixth switching valve 506. The fourth switching valve 504 is connected between the second port of the first bidirectional hydraulic cylinder 101 and the second port of the first directional valve 201; the fifth switching valve 505 is connected between the first port of the second bidirectional hydraulic cylinder 102 and the first port of the second directional valve 202; and the sixth switching valve 506 is connected between the second port of the second bidirectional hydraulic cylinder 102 and the second port of the second directional valve 202.

[0059] like Figure 3 and Figure 9 As shown, in some embodiments, specifically, the main pressure oil pipe includes a first fourth switching valve pipe section 4001 and a second fourth switching valve pipe section 4002. One end of the first fourth switching valve pipe section 4001 is connected to the second first directional valve pipe section 3009, thereby connecting to port B of the first directional valve 201, and the other end of the first fourth switching valve pipe section 4001 is connected to the fourth switching valve 504. One end of the second fourth switching valve pipe section 4002 is connected to the first bidirectional hydraulic cylinder B pipe section 3004, and the other end of the second fourth switching valve pipe section 4002 is connected to the fourth switching valve 504.

[0060] In the embodiments of this application, the first directional valve segment 1, the first switch valve segment, the first bidirectional hydraulic cylinder A segment, the first bidirectional hydraulic cylinder B segment, the fourth switch valve segment 2, the fourth switch valve segment 1, the first directional valve segment 2, and the first directional valve segment 3 are connected sequentially to form a first parallel circuit in parallel operation mode. In the first parallel circuit, the first switch valve 501 and the fourth switch valve 504 are connected. Under the control of the first directional valve 201, independent control of the first bidirectional hydraulic cylinder 101 can be achieved. Simultaneously, the first directional valve 201 can control the hydraulic flow direction in the first parallel circuit, switching the direction to allow the first bidirectional hydraulic cylinder 101 to move in both directions.

[0061] In some embodiments, the main pressure oil pipe further includes a second directional valve section 4003, a fifth switching valve section 4004, a second fifth switching valve section 4005, a first sixth switching valve section 4006, a second sixth switching valve section 4007, and a second directional valve section 4008.

[0062] In the embodiments of this application, the second directional valve 202 has ports A, B, P, and T. Port P is the inlet port, port T is the return port, and ports A and B are working ports. Ports A, B, P, and T of the second directional valve 202 are respectively connected to the fifth switching valve section one, the sixth switching valve section two, the second directional valve section one, and the second directional valve section two. One end of the second directional valve section one is connected to port P of the second directional valve 202, and the other end is connected to the main pressure oil line section. One end of the second directional valve section two is connected to port T of the second directional valve 202, and the other end is connected to the main return oil line section.

[0063] In the embodiments of this application, the main pressure oil pipe section, the first section of the second directional valve pipe, the oil port P of the second directional valve 202, the oil port A of the second directional valve 202, the first section of the fifth switching valve pipe, the fifth switching valve 505, the second section of the fifth switching valve pipe, the second bidirectional hydraulic cylinder A pipe section, the first oil port of the second bidirectional hydraulic cylinder 102, the second oil port of the second bidirectional hydraulic cylinder 102, the second section of the second bidirectional hydraulic cylinder B pipe, the first section of the sixth switching valve pipe, the sixth switching valve 506, the second section of the sixth switching valve pipe, the oil port B of the second directional valve 202, the oil port T of the second directional valve 202, the second section of the second directional valve pipe, and the main return oil pipe section are connected in sequence to form a second parallel circuit in parallel operation mode. In the second parallel circuit, the fifth switching valve 505 and the sixth switching valve 506 are connected, and under the control of the second directional valve 202, independent control of the second bidirectional hydraulic cylinder 102 can be achieved. At the same time, the second directional valve 202 can control the hydraulic flow direction in the second parallel circuit, switch the direction, and make the second bidirectional hydraulic cylinder 102 move in both directions.

[0064] In the embodiments of this application, the first switching valve 501, the fourth switching valve 504, the fifth switching valve 505, and the sixth switching valve 506 are all open, while the other switching valves are closed. The first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 are independently connected between the main pressure oil pipe and the main return oil pipe, forming a parallel working mode. The first bidirectional hydraulic cylinder 101 can be controlled by the first reversing valve 201, and the second bidirectional hydraulic cylinder 102 can be controlled by the second reversing valve 202. In the parallel working mode, the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 can move independently without interference, enabling simultaneous simulation of two objects. In the embodiments of this application, by simultaneously simulating two objects, comparative experiments can be conducted under the same hydraulic station, improving experimental efficiency and ensuring experimental accuracy.

[0065] In some embodiments, serial and parallel modes can provide more flexible and variable loading methods for testing.

[0066] like Figure 4 As shown, in some embodiments, the switching valve includes a seventh switching valve 507, an eighth switching valve 508, a ninth switching valve 509, and a tenth switching valve 510. The seventh switching valve 507 is connected between the first oil port and the second oil port of the first bidirectional hydraulic cylinder 101, the eighth switching valve 508 is connected between the first oil port and the second oil port of the second bidirectional hydraulic cylinder 102, the ninth switching valve 509 is connected between the first oil port and the second oil port of the first inertial loading guide hydraulic cylinder 301, and the tenth switching valve 510 is connected between the first oil port and the second oil port of the second inertial loading guide hydraulic cylinder 302.

[0067] In the embodiments of this application, a seventh switching valve 507 is connected between the first oil port and the second oil port of the first bidirectional hydraulic cylinder 101. When the seventh switching valve 507 is in the connected state, the two oil chambers of the first bidirectional hydraulic cylinder 101 are bypassed. An eighth switching valve 508 is connected between the first oil port and the second oil port of the second bidirectional hydraulic cylinder 102. When the eighth switching valve 508 is in the connected state, the two oil chambers of the second bidirectional hydraulic cylinder 102 are bypassed. A ninth switching valve 509 is connected between the first oil port and the second oil port of the first inertial loading guide hydraulic cylinder 301. When the ninth switching valve 509 is in the connected state, the two oil chambers of the first inertial loading guide hydraulic cylinder 301 are bypassed. A tenth switching valve 510 is connected between the first oil port and the second oil port of the second inertial loading guide hydraulic cylinder 302. When the tenth switching valve 510 is in the connected state, the two oil chambers of the second inertial loading guide hydraulic cylinder 302 are bypassed. Bypass means that the two oil chambers are interconnected. When the first inertial loading guide hydraulic cylinder 301 and the second inertial loading guide hydraulic cylinder 302 are performing inertial loading, the ninth switching valve 509 and the tenth switching valve 510 are in the open state. When the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 are loading, the seventh switching valve 507 and the eighth switching valve 508 are in the open state.

[0068] like Figure 4 and Figure 10 As shown, in some embodiments, the main pressure oil pipe further includes a seventh switching valve section 1 5001 and a seventh switching valve section 2 5002. One end of the seventh switching valve section 1 is connected to the seventh switching valve 507, and the other end is connected to the second bidirectional hydraulic cylinder A section. One end of the seventh switching valve section 2 is connected to the seventh switching valve 507, and the other end is connected to the second bidirectional hydraulic cylinder B section. In the embodiments of this application, by connecting the seventh switching valve 507 to the A and B chambers of the second bidirectional hydraulic cylinder 102, the two chambers of the second bidirectional hydraulic cylinder 102 can be directly interconnected.

[0069] In some embodiments, the main pressure oil pipe further includes an eighth switch valve section 1 5003 and an eighth switch valve section 2 5004. One end of the eighth switch valve section 1 is connected to the eighth switch valve 508, and the other end is connected to the first bidirectional hydraulic cylinder A section. One end of the eighth switch valve section 2 is connected to the eighth switch valve 508, and the other end is connected to the first bidirectional hydraulic cylinder B section. In the embodiments of this application, by connecting the eighth switch valve 508 to the A and B chambers of the first bidirectional hydraulic cylinder 101, the two chambers of the first bidirectional hydraulic cylinder 101 can be directly interconnected.

[0070] In the embodiments of this application, by connecting the two chambers of the first or second bidirectional hydraulic cylinder to each other, in parallel operation mode, the first and second bidirectional hydraulic cylinders can move independently without interference, and can also simultaneously connect to the same object, allowing the first bidirectional hydraulic cylinder to operate at high pressure while the second bidirectional hydraulic cylinder bypasses, or vice versa. In the embodiments of this application, the bypass control of the first and second bidirectional hydraulic cylinders can be achieved through the seventh and eighth switching valves, allowing the first and second bidirectional hydraulic cylinders to work alternately in a cyclical manner, maintaining high-precision load simulation and improving the reliability and continuity of the test.

[0071] In some embodiments, the first inertial loading guide hydraulic cylinder 301 includes chamber A and chamber B, with chamber A having a first oil port and chamber B having a second oil port. The main pressure oil pipe further includes a first ninth switching valve section 5005 and a second ninth switching valve section 5006, a first inertial loading guide hydraulic cylinder section A 5007, and a first inertial loading guide hydraulic cylinder section B 5008. One end of the first ninth switching valve section is connected to the ninth switching valve 509, and the other end is connected to the first inertial loading guide hydraulic cylinder section A, which is connected to the first oil port of the first inertial loading guide hydraulic cylinder 301. One end of the second ninth switching valve section is connected to the ninth switching valve 509, and the other end is connected to the first inertial loading guide hydraulic cylinder section B, which is connected to the second oil port of the first inertial loading guide hydraulic cylinder 301. In the embodiments of this application, the first oil port and the second oil port of the first inertial loading guide hydraulic cylinder 301 are connected through the ninth switching valve 509, so that the two chambers of the first inertial loading guide hydraulic cylinder 301 can be directly connected to each other.

[0072] In some embodiments, the first inertial loading motor 401 is connected between the first inertial loading guide hydraulic cylinder A section and the first inertial loading guide hydraulic cylinder B section, thereby connecting to the two oil chambers of the first inertial loading guide hydraulic cylinder 301. That is, the first inertial loading motor 401 and the ninth switching valve 509 are connected in parallel between the first oil port and the second oil port of the first inertial loading guide hydraulic cylinder 301.

[0073] In some embodiments, the second inertial loading guide hydraulic cylinder 302 includes chamber A and chamber B, with chamber A having a first oil port and chamber B having a second oil port. The main pressure oil pipe further includes a tenth switch valve section 1 5009 and a tenth switch valve section 2 5010, a second inertial loading guide hydraulic cylinder section A 5011, and a second inertial loading guide hydraulic cylinder section B 5012. One end of the tenth switch valve section 1 is connected to the tenth switch valve 510, and the other end is connected to the second inertial loading guide hydraulic cylinder section A, which is connected to the first oil port of the second inertial loading guide hydraulic cylinder 302. One end of the tenth switch valve section 2 is connected to the ninth switch valve 509, and the other end is connected to the second inertial loading guide hydraulic cylinder section B, which is connected to the second oil port of the second inertial loading guide hydraulic cylinder 302. In the embodiments of this application, the first and second oil ports of the second inertial loading guide hydraulic cylinder 302 are connected through the tenth switching valve 510, so that the two chambers of the second inertial loading guide hydraulic cylinder 302 can be directly connected to each other.

[0074] In some embodiments, the second inertial loading motor 402 is connected between the A section of the second inertial loading guide hydraulic cylinder and the B section of the second inertial loading guide hydraulic cylinder, thereby connecting to the two oil chambers of the second inertial loading guide hydraulic cylinder 302. That is, the second inertial loading motor 402 and the tenth switching valve 510 are connected in parallel between the first oil port and the second oil port of the second inertial loading guide hydraulic cylinder 302.

[0075] In the embodiments of this application, the first and second oil ports of the first inertial loading guide hydraulic cylinder are directly connected through the ninth switching valve, allowing the two chambers of the first inertial loading guide hydraulic cylinder to communicate with each other. Similarly, the first and second oil ports of the second inertial loading guide hydraulic cylinder are directly connected through the tenth switching valve, allowing the two chambers of the second inertial loading guide hydraulic cylinder to communicate with each other. This allows the first and second inertial loading guide hydraulic cylinders to lose their inertial force without unloading the inertial wheels of the first and second inertial loading motors, thereby enhancing controllability and safety.

[0076] In some embodiments, all of the plurality of switching valves are ball valves. In some embodiments, the switching valves are electrically controlled switching valves. In the embodiments of this application, the plurality of switching valves are ball valves, which have a simple structure, reliable control, and can meet the requirements of high pressure and high flow.

[0077] In some embodiments, both the first directional valve 201 and the second directional valve 202 are three-position four-way solenoid directional valves. In some embodiments, both the first directional valve 201 and the second directional valve 202 are servo directional valves. In the embodiments of this application, the servo directional valves can control the flow and pressure of a high-pressure, high-flow hydraulic system. In the embodiments of this application, the servo directional valves can precisely control pressure, flow, and direction, ensuring the accuracy and real-time performance of load simulation.

[0078] In the embodiments of this application, the entire hydraulic system has only two directional valves, namely the first directional valve 201 and the second directional valve 202, which can realize the switching of multiple working modes and hydraulic circuits of the hydraulic system.

[0079] In some embodiments, the first inertial loading motor 401 and the second inertial loading motor 402 are bidirectional vane pumps. In the embodiments of this application, the use of bidirectional vane pumps enables bidirectional passive loading of the first inertial loading guide hydraulic cylinder 301 and the second inertial loading guide hydraulic cylinder 302, accommodating the bidirectional movement of the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102. By using bidirectional vane pumps to provide inertial force to the inertial loading guide hydraulic cylinders, when the movement directions of the first and second inertial loading guide hydraulic cylinders change, the rotation directions of the first and second inertial loading motors remain unchanged under the action of the inertial wheel, providing resistance opposite to the direction of movement, thus simulating the effect of real inertial force.

[0080] In some embodiments, two pilot-operated electrically controlled relief valves 701 and 702 are connected between the first oil port and the second oil port of the first bidirectional hydraulic cylinder 101. Two pilot-operated electrically controlled relief valves 703 and 704 are connected between the first oil port and the second oil port of the second bidirectional hydraulic cylinder 102.

[0081] In the embodiments of this application, two pilot-operated electrically controlled relief valves 701 and 702 are connected in parallel between the first oil port and the second oil port of the first bidirectional hydraulic cylinder 101, and the connection directions are opposite. The two pilot-operated electrically controlled relief valves 701 and 702 can achieve safe control in two directions. Moreover, the use of pilot-operated electrically controlled relief valves makes the control more efficient, enables remote control, and can also be remotely activated when needed, even when the pressure is below a preset threshold, to meet the usage requirements of special application scenarios.

[0082] In the embodiments of this application, two pilot-operated electrically controlled relief valves 703 and 704 are connected in parallel between the first and second oil ports of the second bidirectional hydraulic cylinder 102, and the connection directions are opposite. The two pilot-operated electrically controlled relief valves 703 and 704 can achieve safe control in two directions. Moreover, the use of pilot-operated electrically controlled relief valves makes the control more efficient, enables remote control, and can also be remotely activated when needed, even when the pressure is below a preset threshold, to meet the usage requirements of special application scenarios.

[0083] In some embodiments, the relief valve also has a pressure stabilizing function. The threshold pressure of the relief valve can be set as the target pressure of the bidirectional hydraulic cylinder, and the output pressure of the directional valve can be adjusted to be greater than the target pressure. Under the action of the relief valve, the input pressure of the bidirectional hydraulic cylinder can be maintained at the target pressure.

[0084] In some embodiments, two relief valves 801 and 802 are connected between the first and second oil ports of the first inertial loading guide hydraulic cylinder 301. Two relief valves 803 and 804 are connected between the first and second oil ports of the second inertial loading guide hydraulic cylinder 302. In embodiments of this application, the two relief valves 801 and 802 connecting the first and second oil ports of the first inertial loading guide hydraulic cylinder 301 are connected in parallel with opposite connection directions. The two relief valves can achieve safety control in two directions. The two relief valves 803 and 804 connecting the first and second oil ports of the second inertial loading guide hydraulic cylinder 302 are connected in parallel with opposite connection directions. The two relief valves can achieve safety control in two directions, preventing system damage caused by excessively high inertial wheel speed.

[0085] In some embodiments, the hydraulic system further includes multiple pressure sensors. Specifically, the pressure sensors include a first pressure sensor 601, a second pressure sensor 602, a third pressure sensor 603, a fourth pressure sensor 604, a fifth pressure sensor 605, a sixth pressure sensor 606, a seventh pressure sensor 607, and an eighth pressure sensor 608. Each port of the first bidirectional hydraulic cylinder 101, the second bidirectional hydraulic cylinder 102, the first inertial loading guide hydraulic cylinder 301, and the second inertial loading guide hydraulic cylinder 302 is connected to a pressure sensor.

[0086] In some embodiments, specifically, a first pressure sensor 601 is connected to a first oil port of a first bidirectional hydraulic cylinder 101, and a second pressure sensor 602 is connected to a second oil port of the first bidirectional hydraulic cylinder 101.

[0087] The third pressure sensor 603 is connected to the first oil port of the second bidirectional hydraulic cylinder 102, and the fourth pressure sensor 604 is connected to the second oil port of the second bidirectional hydraulic cylinder 102.

[0088] The fifth pressure sensor 605 is connected to the first oil port of the first inertial loading guide hydraulic cylinder 301, and the sixth pressure sensor 606 is connected to the second oil port of the first inertial loading guide hydraulic cylinder 301.

[0089] The seventh pressure sensor 607 is connected to the first oil port of the second inertial loading guide hydraulic cylinder 302, and the eighth pressure sensor 608 is connected to the second oil port of the second inertial loading guide hydraulic cylinder 302.

[0090] In the embodiments of this application, the working pressure of each oil chamber is detected by multiple pressure sensors.

[0091] In some embodiments, a one-way valve is provided between each pressure sensor and its corresponding oil chamber. In the embodiments of this application, by providing a one-way valve, the one-way valve is open when the pressure sensor is in the detection state, and closed at other times, which can effectively protect the pressure sensor and ensure the stability of the applied pressure.

[0092] In some embodiments, the hydraulic system further includes an auxiliary pressure line Y. Both the first directional valve 201 and the second directional valve 202 are electro-hydraulic servo valves. In some embodiments, both directional valves are connected to the auxiliary pressure line. Figure 1 As shown, both the first directional valve 201 and the second directional valve 202 include an X port and a Y port. The X port is connected to the main pressure oil pipe P, and the Y port is connected to the auxiliary pressure oil pipe Y. The X port and the Y port serve as the hydraulic control ports of the electro-hydraulic servo valve. In the embodiments of this application, through the control of the electro-hydraulic servo valve, the entire hydraulic system has a fast dynamic response, high control accuracy, and long service life.

[0093] In some embodiments, a high-pressure, high-flow-rate inertial load hydraulic test bench is also provided, the high-pressure, high-flow-rate inertial load hydraulic test bench including the hydraulic system 2000 as described in any of the above embodiments. A first bidirectional hydraulic cylinder is connected to a first inertial loading guide hydraulic cylinder, and a first inertial loading motor is connected to the first inertial loading guide hydraulic cylinder. A second bidirectional hydraulic cylinder is connected to a second inertial loading guide hydraulic cylinder, and a second inertial loading motor is connected to the second inertial loading guide hydraulic cylinder. The first inertial loading guide hydraulic cylinder and the second inertial loading guide hydraulic cylinder are connected to the same drive system, or the first inertial loading guide hydraulic cylinder and the second inertial loading guide hydraulic cylinder are connected to different drive systems.

[0094] In the embodiments of this application, the first inertial loading guide hydraulic cylinder and the second inertial loading guide hydraulic cylinder can be directly connected to the drive system via couplings. The first bidirectional hydraulic cylinder and the first inertial loading guide hydraulic cylinder can be connected via couplings. The second bidirectional hydraulic cylinder and the second inertial loading guide hydraulic cylinder can be connected via couplings.

[0095] like Figure 5 As shown, specifically, in some embodiments, the high-pressure, high-flow-rate inertial load hydraulic test bench 1000 includes a drive system 1001, an inertial force load simulation system 1003, and a load simulation system 1002. The inertial force load simulation system 1003 and the load simulation system 1002 are components of the aforementioned hydraulic system 2000. Specifically, the inertial force loading simulation system is positioned between the drive system and the load simulation system to simulate the inertial force experienced by the drive system. The load simulation system 1002 is used to simulate the load experienced by the test object in a real environment, testing the performance of the test object under actual working conditions. The inertial force load simulation system 1003 is used to simulate different inertial forces applied to the test object, testing the performance and stability of the test object under dynamic working conditions such as start-stop and reversal, as well as its reliability under repeated inertial impact loads. The drive system 1001 includes a drive hydraulic cylinder. The inertial force load simulation system 1003 includes a first inertial loading guide hydraulic cylinder 301, a second inertial loading guide hydraulic cylinder 302, a first inertial loading motor 401, and a second inertial loading motor 402, as described in any of the above embodiments. The load simulation system 1002 includes a first bidirectional hydraulic cylinder 101, a second bidirectional hydraulic cylinder 102, a first directional valve 201, and a second directional valve 202, as described in any of the above embodiments.

[0096] refer to Figure 6 In the embodiments of this application, the first bidirectional hydraulic cylinder 101 is connected to the first inertial loading guide hydraulic cylinder 301, and the second bidirectional hydraulic cylinder 102 is connected to the second inertial loading guide hydraulic cylinder 302. The first inertial loading motor 401 and the second inertial loading motor 402 are respectively connected to the first inertial loading guide hydraulic cylinder 301 and the second inertial loading guide hydraulic cylinder 302. In the embodiments of this application, the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder are simultaneously connected to a drive system. Specifically, the drive system includes drive hydraulic cylinders. The first inertial loading motor 401 and the second inertial loading motor 402 can be respectively connected to the first inertial wheel 4011 and the second inertial wheel 4021. In the embodiments of this application, by arranging the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder in parallel, the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder can work in parallel or in series, which can meet the needs of high-pressure and high-flow drive load simulation of the drive system.

[0097] In some embodiments, specifically, the load simulation system 1002 of the high-pressure, high-flow-rate inertial load hydraulic test bench includes a first bidirectional hydraulic cylinder 101 and a second bidirectional hydraulic cylinder 102, a first reversing valve 201, a second reversing valve 202, and multiple switching valves. The multiple switching valves include a first switching valve, a second switching valve, a third switching valve, a fourth switching valve, a fifth switching valve, a sixth switching valve, a seventh switching valve, an eighth switching valve, a ninth switching valve, and a tenth switching valve. When the corresponding switching valves are connected, causing the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 to operate in series, the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 can synchronously perform load testing on the test object, i.e., the drive system, and switch the movement direction of the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 through the first reversing valve 201. The series operation of the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 can meet the needs of high-pressure, high-load drive load simulation of the drive system 1001.

[0098] In some embodiments, when the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 operate in series, the ninth and tenth switching valves can be opened or closed independently. For example, when the ninth switching valve is closed and the tenth switching valve is open, the first inertial loading motor 401 is connected to the first inertial wheel 4011 to simulate inertial force, while the second inertial loading motor 402 does not provide inertial force. In some embodiments, the ninth and tenth switching valves can be alternately closed and open, allowing the first inertial loading motor 401 and the second inertial loading motor 402 to alternately simulate inertial force. In some embodiments, the ninth and tenth switching valves can be closed simultaneously, allowing the first inertial loading motor 401 and the second inertial loading motor 402 to work together to simulate inertial force. In some embodiments, the masses of the first inertial wheel 4011 and the second inertial wheel 4021 can be different to simulate sudden changes in load mass. In the embodiments of this application, while the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 are continuously loaded, the mass of the first inertia wheel 4011 and the second inertia wheel 4021 can be changed, or the connection state of the ninth switch valve and the tenth switch valve can be changed, thereby simulating different inertial force conditions.

[0099] In some embodiments, specifically, the first and second bidirectional hydraulic cylinders are arranged in parallel, and can be connected in parallel and work independently to meet the simulation of high-flow-rate drive loads in the drive system. Furthermore, the first and second bidirectional hydraulic cylinders can alternately and cyclically apply loads to meet stable and constant load requirements. In some embodiments, the first bidirectional hydraulic cylinder can also apply a fixed pressure to simulate a constant and stable fixed load, while the second bidirectional hydraulic cylinder applies a dynamic pressure to simulate random and dynamically changing loads. In the embodiments of this application, the high-pressure, high-flow-rate inertial load hydraulic test bench can accurately, stably, and with multiple requirements for simulating loads and inertial forces, offering high safety, strong adaptability, and convenient operation.

[0100] In some embodiments of this application, a high-pressure, high-flow-rate inertial load hydraulic test method is provided. This test method employs the high-pressure, high-flow-rate inertial load hydraulic test bench described in any of the above embodiments.

[0101] In some embodiments, the high-pressure, high-flow-rate inertial load hydraulic test bench includes a first bidirectional hydraulic cylinder, a second bidirectional hydraulic cylinder, and multiple switching valves. The multiple switching valves include a first switching valve, a second switching valve, a third switching valve, a fourth switching valve, a fifth switching valve, a sixth switching valve, a seventh switching valve, an eighth switching valve, a ninth switching valve, and a tenth switching valve. The test method includes: the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder are simultaneously connected to a drive system; the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder operate in a series working mode, or in a parallel working mode, or switch between a series working mode and a parallel working mode.

[0102] In some embodiments, when the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder are in series operation mode, the ninth switching valve is closed and the tenth switching valve is open, the first inertial loading motor is connected to the first inertial wheel to simulate inertial force, and the second inertial loading motor does not provide inertial force.

[0103] In some embodiments, when the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder are in series operation mode, the ninth switching valve is connected and the tenth switching valve is closed, the second inertial loading motor is connected to the second inertial wheel to simulate inertial force, and the first inertial loading motor does not provide inertial force.

[0104] In some embodiments, when the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder are in series operation mode, the ninth switching valve is connected and the tenth switching valve is closed, the second inertial loading motor is connected to the second inertial wheel to simulate inertial force, and the first inertial loading motor does not provide inertial force.

[0105] In some embodiments, the first inertia wheel and the second inertia wheel have different masses. In a series operation mode, the first and second bidirectional hydraulic cylinders keep the ninth switching valve closed and the tenth switching valve open during a first time period; then, during a second time period, the tenth switching valve is closed to simulate the inertial force caused by a sudden change in load mass. The second time period is continuous with the first time period, meaning the start time of the second time period is the same as the end time of the first time period.

[0106] In some embodiments, the first inertia wheel is replaced during the period when the ninth switch valve is open, thereby changing the mass of the first inertia wheel; in some embodiments, the second inertia wheel is replaced during the period when the tenth switch valve is open, thereby changing the mass of the second inertia wheel. In the embodiments of this application, the corresponding inertia wheel can be replaced during the period when the ninth or tenth switch valve is open, thereby simulating different load mass inertial forces without stopping the test bench.

[0107] In some embodiments, in parallel operation mode, the first and second bidirectional hydraulic cylinders are simultaneously connected to a drive system, and they alternately and cyclically apply loads. In the embodiments of this application, by controlling the first and second directional valves, the loading switching cycle, magnitude, and direction of the first and second bidirectional hydraulic cylinders are adjusted, thereby achieving accurate simulation of the load and meeting stable and constant loading requirements.

[0108] In some embodiments, a first bidirectional hydraulic cylinder applies a fixed pressure to simulate a constant and stable fixed load, while a second bidirectional hydraulic cylinder applies a dynamic pressure to simulate a random and dynamically changing load. In the embodiments of this application, the loading pressure magnitude and direction of the first and second bidirectional hydraulic cylinders are adjusted by controlling a first and a second directional valve, thereby achieving accurate simulation of the load. During the experiment, the amplitude and period of the dynamic loading can be adjusted according to actual needs, making the test conditions closer to the real operating environment and improving the simulation accuracy and applicability of the test bench.

[0109] It is understood that, in the embodiments of this application, similar to the series operation mode, in the parallel operation mode, the first inertial loading motor and the second inertial loading motor can also perform corresponding inertial force simulation under the control of the ninth and tenth switching valves.

[0110] refer to Figure 7In some embodiments, when the corresponding switching valves are connected so that the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 are in parallel working mode, the two tested objects, namely the first drive system 1011 and the second drive system 1021, can be loaded and tested. The moving directions of the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 can be controlled by the first reversing valve 201 and the second reversing valve 202, respectively.

[0111] In some embodiments, the inertial load simulation system 1003 of the high-pressure, high-flow-rate inertial load hydraulic test bench includes a first inertial loading guide hydraulic cylinder 301, a second inertial loading guide hydraulic cylinder 302, a first inertial loading motor 401, and a second inertial loading motor 402. The first inertial loading motor 401 controls the first inertial load guide hydraulic cylinder to generate a load of a first target inertia, which is applied to a first test object to measure the performance and reliability of the first test object. The second inertial loading motor 402 controls the second inertial load guide hydraulic cylinder to generate a load of a second target inertia, which is applied to a second test object to measure the performance and reliability of the second test object. The first and second target inertia are inertias determined by the test scenario and can be periodically changing inertia. For example, when simulating the inertial action of the test object during start-up and shutdown, the inertial load guide hydraulic cylinder needs to periodically generate a load corresponding to the inertia during start-up and shutdown. For instance, when testing reliability, the inertial load guide hydraulic cylinder needs to simulate periodically or continuously changing loads, which can be achieved by controlling the inertial loading motor. The first inertial loading guide hydraulic cylinder 301 and the second inertial loading guide hydraulic cylinder 302 can realize the loading requirements of periodic or continuous changes, which can meet the needs of high pressure and high flow drive load simulation of drive system 1001.

[0112] In some embodiments of this application, a high-pressure, high-flow-rate inertial load hydraulic test method is also provided. This test method employs the high-pressure, high-flow-rate inertial load hydraulic test bench described in any of the above embodiments. In some embodiments, the high-pressure, high-flow-rate inertial load hydraulic test bench includes a first bidirectional hydraulic cylinder, a second bidirectional hydraulic cylinder, and multiple switching valves. The multiple switching valves include a first switching valve, a second switching valve, a third switching valve, a fourth switching valve, a fifth switching valve, a sixth switching valve, a seventh switching valve, an eighth switching valve, a ninth switching valve, and a tenth switching valve. The test method includes connecting the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder to a test object, respectively.

[0113] In the embodiments of this application, the first bidirectional hydraulic cylinder is connected to the first drive system, the first bidirectional hydraulic cylinder is connected to the second drive system, the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder work in parallel working mode, and a comparative test is conducted on the first drive system and the second drive system.

[0114] In some embodiments, the high-pressure, high-flow-rate inertial load hydraulic test bench can be used for simulating a ship's propulsion system. The drive system 1001 can be the ship's propulsion system. In some embodiments, the high-pressure, high-flow-rate inertial load hydraulic test bench can be used for simulating a ship's hatch propulsion system. The drive system 1001 can be the hydraulic actuator of a ship's hatch.

[0115] Those skilled in the art will readily understand that the above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A hydraulic system, characterized in that, The hydraulic system includes: The loading cylinder includes a first bidirectional hydraulic cylinder and a second bidirectional hydraulic cylinder. The first bidirectional hydraulic cylinder has two pilot-operated electrically controlled relief valves connected in parallel between its first oil port and its second oil port, and the second bidirectional hydraulic cylinder has two pilot-operated electrically controlled relief valves connected in parallel between its first oil port and its second oil port. A reversing valve, connected to the loading cylinder, includes a first reversing valve and a second reversing valve; First inertia loading guide hydraulic cylinder; Second inertial loading guide hydraulic cylinder; A first inertial loading motor is connected between the first oil port and the second oil port of the first inertial loading guide hydraulic cylinder. The second inertial loading motor is connected between the first oil port and the second oil port of the second inertial loading guide hydraulic cylinder. The first inertial loading motor and the second inertial loading motor are bidirectional vane pumps; The first inertial loading motor is connected to a first inertial wheel; The second inertial loading motor is connected to a second inertial wheel; The first inertia wheel and the second inertia wheel have different masses; multiple switching valves are used to switch the connection relationship between the loading cylinder and the reversing valve, and under the action of the reversing valve, the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder can achieve bypass working mode, series working mode, and parallel working mode; Two inertial loading guide hydraulic cylinders are used to simulate different inertial forces by using an inertial loading motor and a switching valve respectively. The inertial loading motor is adjusted to quickly control the load on the inertial loading guide hydraulic cylinders, thereby enabling the inertial loading guide hydraulic cylinders to simulate different inertial forces. By controlling the load of the two loading cylinders and the two inertial loading guide hydraulic cylinders, the hydraulic system can simulate a high-pressure, high-flow-rate inertial load hydraulic test.

2. The hydraulic system according to claim 1, characterized in that, The switching valve includes a first switching valve, a second switching valve, and a third switching valve. The first switching valve is connected between the first oil port of the first bidirectional hydraulic cylinder and the first interface of the first directional valve. The second switching valve is connected between the first oil port of the second bidirectional hydraulic cylinder and the second interface of the first directional valve. The third switching valve is connected between the second oil port of the first bidirectional hydraulic cylinder and the second oil port of the second bidirectional hydraulic cylinder.

3. The hydraulic system according to claim 2, characterized in that, The switching valve includes a fourth switching valve, a fifth switching valve, and a sixth switching valve. The fourth switching valve is connected between the second oil port of the first bidirectional hydraulic cylinder and the second port of the first directional valve. The fifth switching valve is connected between the first oil port of the second bidirectional hydraulic cylinder and the first port of the second directional valve. The sixth switching valve is connected between the second oil port of the second bidirectional hydraulic cylinder and the second port of the second directional valve.

4. The hydraulic system according to claim 3, characterized in that, The switching valves include a seventh switching valve, an eighth switching valve, a ninth switching valve, and a tenth switching valve. The seventh switching valve is connected between the first oil port and the second oil port of the first bidirectional hydraulic cylinder, the eighth switching valve is connected between the first oil port and the second oil port of the second bidirectional hydraulic cylinder, the ninth switching valve is connected between the first oil port and the second oil port of the first inertial loading guide hydraulic cylinder, and the tenth switching valve is connected between the first oil port and the second oil port of the second inertial loading guide hydraulic cylinder.

5. The hydraulic system according to claim 1, characterized in that, All of the multiple switching valves are ball valves, and the switching valves are electrically controlled switching valves; Both the first and second directional control valves are three-position four-way solenoid directional control valves, and both are servo directional control valves.

6. The hydraulic system according to any one of claims 1-5, characterized in that, The hydraulic system also includes multiple pressure sensors and multiple check valves. Each oil port of the first bidirectional hydraulic cylinder, the second bidirectional hydraulic cylinder, the first inertial loading guide hydraulic cylinder, and the second inertial loading guide hydraulic cylinder is connected to a pressure sensor, and a check valve is provided between each pressure sensor and its corresponding oil port.

7. A high-pressure, high-flow-rate inertial load hydraulic test bench, characterized in that, The high-pressure, high-flow-rate inertial load hydraulic test bench includes the hydraulic system according to any one of claims 1-6; The first bidirectional hydraulic cylinder is connected to the first inertial loading guide hydraulic cylinder, and the first inertial loading motor is connected to the first inertial loading guide hydraulic cylinder; The second bidirectional hydraulic cylinder is connected to the second inertial loading guide hydraulic cylinder, and the second inertial loading motor is connected to the second inertial loading guide hydraulic cylinder; The first inertial loading guide hydraulic cylinder and the second inertial loading guide hydraulic cylinder are connected to the same drive system, or the first inertial loading guide hydraulic cylinder and the second inertial loading guide hydraulic cylinder are connected to different drive systems.

8. A high-pressure, high-flow-rate hydraulic test method for inertial loads, characterized in that, The high-pressure, high-flow-rate inertial load hydraulic test method employs the high-pressure, high-flow-rate inertial load hydraulic test bench according to claim 7, and the test method includes: The first and second bidirectional hydraulic cylinders are simultaneously connected to a drive system. The first and second bidirectional hydraulic cylinders work in series, or in parallel, or switch between series and parallel working modes. Alternatively, the first bidirectional hydraulic cylinder is connected to the first drive system, and the first bidirectional hydraulic cylinder is connected to the second drive system. The first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder work in parallel operation mode, and a comparative test is conducted on the first drive system and the second drive system.

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