Hydraulic system, high-pressure large-flow inertia load hydraulic test bed and method

Abstract

The invention discloses a hydraulic system and a high-pressure large-flow inertia load hydraulic test bench and method, and the hydraulic system comprises a loading oil cylinder which comprises a first bidirectional hydraulic cylinder and a second bidirectional hydraulic cylinder; the reversing valve is connected with the loading oil cylinder and comprises a first reversing valve and a second reversing valve; a first inertia loading guide hydraulic cylinder; a second inertia loading guide hydraulic cylinder; the first inertia loading motor is connected between the two oil ports of the first inertia loading guide hydraulic cylinder; the second inertia loading motor is connected between the two oil ports of the second inertia loading guide hydraulic cylinder; and the plurality of switch valves are used for switching the connection relationship between the loading oil cylinder and the reversing valve, and under the action of the reversing valve, the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder realize a bypass working mode, a series working mode and a parallel working mode.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of high-pressure large-flow hydraulic systems and inertial load testing, and particularly relates to a hydraulic system, a high-pressure large-flow inertial load hydraulic test bench and a method. BACKGROUND

[0002] With the rise of marine engineering, there are more and more large-inertia load devices on ship and underwater equipment major engineering equipment, and the test bench needs to realize large-inertia load loading while realizing load simulation. Most of the existing hydraulic loading test benches can only meet the load simulation of a single actuator through pressure and flow regulation, and cannot meet the high-pressure large-flow inertial load hydraulic simulation experiment. In the prior art, mechanical inertia is generally directly used to realize inertial loading by directly connecting a flywheel or a mass block with a load. This method has poor safety and is inconvenient to adjust. In the prior art, there is also an electric inertia that realizes inertial loading by using a loading motor, but it cannot meet the inertial load simulation of a high-pressure large-flow hydraulic system. Of course, in the prior art, there are also hydraulic test benches that use hydraulic methods and hydraulic motors for inertial loading. However, the inertial loading is arranged behind the load, and can only be used for rotating loads, cannot simulate the movement of the hydraulic cylinder, has poor time-domain matching and replaceability in inertial simulation, and cannot simulate the real inertial force, so it cannot meet the high-pressure large-flow inertial load hydraulic simulation experiment. SUMMARY

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

[0004] To achieve the above object, the present application adopts the following technical scheme.

[0005] In some embodiments, a hydraulic system is provided, which comprises: a loading oil cylinder comprising a first bidirectional hydraulic cylinder and a second bidirectional hydraulic cylinder; a reversing valve connected to the loading oil cylinder, comprising a first reversing valve and a second reversing valve; a first inertial loading guide hydraulic cylinder; a second inertial loading guide hydraulic cylinder; a first inertial loading motor connected between a first oil port and a second oil port of the first inertial loading guide hydraulic cylinder; a second inertial loading motor connected between a first oil port and a second oil port of the second inertial loading guide hydraulic cylinder; A plurality of switch valves are used to switch the connection relationship between the loading oil cylinder and the reversing valve, and under the action of the reversing valve, the first and second bidirectional hydraulic cylinders realize bypass working mode, series working mode and parallel working mode.

[0006] In some embodiments, the switch valve includes a first switch valve, a second switch valve and a third switch valve, wherein the first switch valve is connected between the first oil port of the first bidirectional hydraulic cylinder and the first interface of the first reversing valve, the second switch valve is connected between the first oil port of the second bidirectional hydraulic cylinder and the second interface of the first reversing valve, and the third switch 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.

[0007] In some embodiments, the switch valve includes a fourth switch valve, a fifth switch valve and a sixth switch valve, wherein the fourth switch valve is connected between the second oil port of the first bidirectional hydraulic cylinder and the second interface of the first reversing valve, the fifth switch valve is connected between the first oil port of the second bidirectional hydraulic cylinder and the first interface of the second reversing valve, and the sixth switch valve is connected between the second oil port of the second bidirectional hydraulic cylinder and the second interface of the second reversing valve.

[0008] In some embodiments, the switch valve includes a seventh switch valve, an eighth switch valve, a ninth switch valve and a tenth switch valve, wherein the seventh switch valve is connected between the first and second oil ports of the first bidirectional hydraulic cylinder, the eighth switch valve is connected between the first and second oil ports of the second bidirectional hydraulic cylinder, the ninth switch valve is connected between the first and second oil ports of the first inertia loading guide hydraulic cylinder, and the tenth switch valve is connected between the first and second oil ports of the second inertia loading guide hydraulic cylinder.

[0009] In some embodiments, the plurality of switch valves are ball valves, and the ball valves are electrically controlled switch valves.

[0010] In some embodiments, the first and second reversing valves are three-position four-way electromagnetic reversing valves, and the first and second reversing valves are servo reversing valves.

[0011] In some embodiments, the first and second inertia loading motors are bidirectional vane pumps.

[0012] In some embodiments, two pilot-controlled electrically controlled overflow valves with opposite directions are connected in parallel between the first and second oil ports of the first bidirectional hydraulic cylinder. Two pilot-controlled electrically controlled overflow valves with opposite directions are connected in parallel between the first and second oil ports of the second bidirectional hydraulic cylinder.

[0013] In some embodiments, the hydraulic system further comprises a plurality of pressure sensors and a plurality of one-way valves, one pressure sensor is connected to each oil port of the first bidirectional hydraulic cylinder, the second bidirectional hydraulic cylinder, the first inertia loading guide hydraulic cylinder and the second inertia loading guide hydraulic cylinder, and a one-way valve is arranged between each pressure sensor and the corresponding oil port.

[0014] In some embodiments, a high-pressure and large-flow inertia load hydraulic test bench is also provided, which comprises the hydraulic system according to any one of the above.

[0015] Compared with the prior art, the beneficial effects of the present application are at least: in the embodiments of the present application, the working mode switching of the parallel working or series working of the two loading cylinders is realized through the two reversing valves and the plurality of on-off valves, so as to realize different loading requirements. In the embodiments of the present application, the simulation of different inertial forces is realized by the two inertia loading guide hydraulic cylinders through one inertia loading motor and one on-off valve respectively, and the quick regulation and simulation of the inertia load of the inertia loading guide hydraulic cylinder can be realized by regulating and controlling the inertia load mass of the inertia loading motor, so that the inertia loading guide hydraulic cylinder simulates different inertial forces, and the controllable regulation of the loads of the two loading cylinders and the two inertia loading guide hydraulic cylinders enables the whole hydraulic system to realize the simulation of high-pressure and large-flow inertia load hydraulic test. In the embodiments of the present application, the moving inertia load is replaced by the rotating inertia load, and the moving load is converted through the setting of the inertia loading motor and the inertia loading guide hydraulic cylinder. The inertia load itself and the inertia loading guide hydraulic cylinder are decoupled, the rotating inertia load mass can be directly replaced, various load inertial forces suffered by the moving hydraulic cylinder can be simulated conveniently, and the safety is high. Moreover, through the decoupling setting, the problem of difficult guidance of the moving load is avoided, and the error caused by the guidance friction of the moving load is also reduced.

[0016] It can be understood that the description of the beneficial effects of the present application is only a direct description of the beneficial effects in some embodiments of the present application, and the effects of other technical solutions and features of the present application are described with reference to the related description in the specific embodiments. In addition, the technical effects of the related solutions of the present application can be determined without any doubt, and the technical effects of the related solutions of the present application can be determined without any doubt. BRIEF DESCRIPTION OF DRAWINGS

[0017] Figure 1 It is the overall structure schematic diagram of the hydraulic system of one embodiment of the present application.

[0018] Figure 2 It is the overall structure schematic diagram of the hydraulic system of one embodiment of the present application in series working mode.

[0019] Figure 3The overall structure schematic diagram of the hydraulic system of one embodiment of the present application in parallel operation mode.

[0020] Figure 4 The overall structure schematic diagram of the hydraulic system of one embodiment of the present application in bypass operation mode.

[0021] Figure 5 The overall structure schematic diagram of the high-pressure and large-flow inertial load hydraulic test bench of one embodiment of the present application.

[0022] Figure 6 The structure schematic diagram of the high-pressure and large-flow inertial load hydraulic test bench of one embodiment of the present application.

[0023] Figure 7 The structure schematic diagram of the high-pressure and large-flow inertial load hydraulic test bench of one embodiment of the present application.

[0024] Figure 8 The partial structure schematic diagram of the hydraulic system of one embodiment of the present application in series operation mode.

[0025] Figure 9 The partial structure schematic diagram of the hydraulic system of one embodiment of the present application in parallel operation mode.

[0026] Figure 10 The partial structure schematic diagram of the hydraulic system of one embodiment of the present application in bypass operation mode. DETAILED DESCRIPTION

[0027] In order to make the objects, technical solutions and advantages of the present application clearer, the present application will be further described in detail below with reference to the drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and not used to limit the present application.

[0028] In the description of the present specification, the description of the terms "one embodiment", "some embodiments", "an example", "a specific example", or "some examples" means that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present application. In the present specification, the illustrative description of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any appropriate manner in any one or more embodiments or examples. In addition, the skilled in the art can combine and combine the different embodiments or examples described in the present specification and the features of the different embodiments or examples without contradiction.

[0029] 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; A reversing valve, connected to the loading cylinder, includes a first reversing valve 201 and a second reversing valve 202; First inertial loading guide hydraulic cylinder 301; Second inertial loading guide hydraulic cylinder 302; 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. 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. 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.

[0030] 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 1 As 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.

[0031] In some embodiments, the switch valve includes a first switch valve 501, a second switch valve 502, and a third switch valve 503, wherein the first switch valve 501 is connected between the first oil port of the first bidirectional hydraulic cylinder 101 and the first interface of the first reversing valve 201, the second switch valve 502 is connected between the first oil port of the second bidirectional hydraulic cylinder 102 and the second interface of the first reversing valve 201, and the third switch 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.

[0032] In some embodiments, the first reversing valve 201 and the second reversing valve 202 each include a first interface and a second interface, which are working oil ports of the reversing valve. In the embodiments of the present application, as shown in Figure 1 , the oil port A of the first reversing valve 201 is the first interface, and the oil port B is the second interface. The oil port A of the second reversing valve 202 is the first interface, and the oil port B is the second interface. Through the communication of the first switch valve 501, the second switch valve 502, and the third switch valve 503, the series loading of the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 can be realized.

[0033] In some embodiments, as shown in Figure 2 , the first switch valve 501, the second switch valve 502, and the third switch valve 503 are all in the communication position, and the other switch valves are in the closed position, realizing the series loading of the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102, and the first inertia loading motor 401 and the second inertia loading motor 402 can realize the passive inertia force loading of the first inertia loading guide hydraulic cylinder 301 and the second inertia loading guide hydraulic cylinder 302, simulating the inertia force.

[0034] In the embodiments of the present 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 driving system, simulating the same load, realizing double load simulation under the same hydraulic oil source, and keeping the two cylinders synchronized. In some embodiments, the simulated load can be a ship hatch cover. In some embodiments, the first inertia loading motor 401 and the second inertia loading motor 402 are connected to an inertia wheel with the same mass as the simulated load. The inertia wheel is connected to the rotating shafts of the first inertia loading motor 401 and the second inertia loading motor 402.

[0035] As shown in Figure 2As 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.

[0036] 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.

[0037] 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.

[0038] like Figure 2 and Figure 8 As 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.

[0039] 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.

[0040] In some embodiments, the first bidirectional hydraulic cylinder 101 has an A cavity and a B cavity, and the A cavity has a first oil port and the B cavity has a second oil port. One end of the first bidirectional hydraulic cylinder A pipe section is connected with the first switch valve 501, and the other end of the first bidirectional hydraulic cylinder A pipe section is connected with the first oil port of the A cavity of the first bidirectional hydraulic cylinder 101.

[0041] In some embodiments, the second bidirectional hydraulic cylinder 102 has an A cavity and a B cavity, and the A cavity has a first oil port and the B cavity has a second oil port. The first bidirectional hydraulic cylinder B pipe section and the second bidirectional hydraulic cylinder B pipe section have the third switch valve 503 therebetween. One end of the first bidirectional hydraulic cylinder B pipe section is connected with the second oil port of the B cavity of the first bidirectional hydraulic cylinder 101, and the other end of the first bidirectional hydraulic cylinder B pipe section is connected with the third switch valve 503. One end of the second bidirectional hydraulic cylinder B pipe section is connected with the second oil port of the B cavity of the second bidirectional hydraulic cylinder 102, and the other end of the second bidirectional hydraulic cylinder B pipe section is connected with the third switch valve 503.

[0042] In some embodiments, one end of the second bidirectional hydraulic cylinder A pipe section is connected with the first oil port of the A cavity of the second bidirectional hydraulic cylinder 102, and the other end of the second bidirectional hydraulic cylinder A pipe section is connected with one end of the second switch valve pipe section one. The other end of the second switch valve pipe section one is connected with the second switch valve 502. One end of the second switch valve pipe section two is connected with the second switch valve 502, and the other end of the second switch valve pipe section two is connected with the second reversing valve pipe section two.

[0043] In the embodiments of the present application, the first switch valve 501 is the only switch valve connecting the A cavity of the first bidirectional hydraulic cylinder 101 with the oil port A of the first reversing valve 201. The first bidirectional hydraulic cylinder 101 is connected with the first reversing valve 201, which can serve as a master control switch. The first reversing valve 201 controls the direction of hydraulic oil of the entire hydraulic circuit in the series working mode. The second switch valve 502 connects the first oil port of the second bidirectional hydraulic cylinder 102 and the oil port B of the first reversing valve 201, and the third switch valve 503 connects the second oil port of the first bidirectional hydraulic cylinder 101 and the second oil port of the second bidirectional hydraulic cylinder 102, so that when the first switch valve 501, the second switch valve 502 and the third switch valve 503 are connected at the same time, 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 bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 in series can be controlled at the same time by the first reversing valve 201. In the series mode, the loading capacity of the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 is the same, and has the natural loading synchronization feature, which can realize double loading of the simulated load object.

[0044] 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.

[0045] 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.

[0046] 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.

[0047] 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.

[0048] In the embodiment of the present application, the second reversing valve 202 has an oil port A, an oil port B, an oil port P, and an oil port T. The oil port P is an oil inlet port, the oil port T is an oil return port, and the oil port A and the oil port B are working oil ports. The oil port A, the oil port B, the oil port P, and the oil port T of the second reversing valve 202 are connected to the first switch valve pipe section one, the sixth switch valve pipe section two, the second reversing valve pipe section one, and the second reversing valve pipe section two, respectively. One end of the second reversing valve pipe section one is connected to the oil port P of the second reversing valve 202, and the other end is connected to the main pressure oil pipe section. One end of the second reversing valve pipe section two is connected to the oil port T of the second reversing valve 202, and the other end is connected to the main return oil pipe section.

[0049] In the embodiment of the present application, the main pressure oil pipe section, the second reversing valve pipe section one, the oil port P of the second reversing valve 202, the oil port A of the second reversing valve 202, the first switch valve pipe section one, the fifth switch valve 505, the second switch valve pipe section two, 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 bidirectional hydraulic cylinder B pipe section, the first switch valve pipe section one, the sixth switch valve 506, the second switch valve pipe section two, the oil port B of the second reversing valve 202, the oil port T of the second reversing valve 202, the second reversing valve pipe section two, and the main return oil pipe section are connected in sequence to form a second parallel circuit in a parallel working mode. In the second parallel circuit, the fifth switch valve 505 and the sixth switch valve 506 are in communication, and under the control of the second reversing valve 202, independent control of the second bidirectional hydraulic cylinder 102 can be achieved. At the same time, the second reversing valve 202 can control the hydraulic flow direction in the second parallel circuit to switch the direction and make the second bidirectional hydraulic cylinder 102 move bidirectionally.

[0050] In the embodiment of the present application, when the first switch valve 501, the fourth switch valve 504, the fifth switch valve 505, and the sixth switch valve 506 are all open, and the other switch 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 to form 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 and do not interfere with each other, and can respectively simulate two objects simultaneously. In the embodiment of the present application, by simulating two objects simultaneously, a contrast test can be performed under the same hydraulic station to improve test efficiency and ensure test accuracy.

[0051] In some embodiments, the series mode and the parallel mode can provide more flexible and variable loading modes for testing.

[0052] As Figure 4As 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.

[0053] 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.

[0054] 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.

[0055] In some embodiments, the main pressure oil pipe further comprises an eighth switch valve pipe segment one 5003 and an eighth switch valve pipe segment two 5004. One end of the eighth switch valve pipe segment one is connected to the eighth switch valve 508, and the other end of the eighth switch valve pipe segment one is connected to the first bidirectional hydraulic cylinder A pipe segment. One end of the eighth switch valve pipe segment two is connected to the eighth switch valve 508, and the other end of the eighth switch valve pipe segment two is connected to the first bidirectional hydraulic cylinder B pipe segment. In the embodiments of the present application, by connecting the eighth switch valve 508 with the A cavity and the B cavity of the first bidirectional hydraulic cylinder 101, the two cavities of the first bidirectional hydraulic cylinder 101 can be directly connected to each other.

[0056] In the embodiments of the present application, by connecting the two cavities of the first bidirectional hydraulic cylinder or the second bidirectional hydraulic cylinder to each other, in the parallel working mode, the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder can each move independently without interfering with each other, and can also simultaneously connect to the same object, and make the first bidirectional hydraulic cylinder work at high pressure, and the second bidirectional hydraulic cylinder bypass, or the second bidirectional hydraulic cylinder work at high pressure, and the first bidirectional hydraulic cylinder bypass. In the embodiments of the present application, the seventh switch valve and the eighth switch valve can be used to control the bypass of the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder, so that the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder can work alternately and cyclically, and high-precision load simulation can be maintained, and test reliability and continuity can be improved.

[0057] In some embodiments, the first inertia loading guide hydraulic cylinder 301 comprises an A cavity and a B cavity, the A cavity has a first oil port, and the B cavity has a second oil port, and the main pressure oil pipe further comprises a ninth switch valve pipe segment one 5005 and a ninth switch valve pipe segment two 5006, a first inertia loading guide hydraulic cylinder A pipe segment 5007, and a first inertia loading guide hydraulic cylinder B pipe segment 5008. One end of the ninth switch valve pipe segment one is connected to the ninth switch valve 509, and the other end of the ninth switch valve pipe segment one is connected to the first inertia loading guide hydraulic cylinder A pipe segment, which is connected to the first oil port of the first inertia loading guide hydraulic cylinder 301. One end of the ninth switch valve pipe segment two is connected to the ninth switch valve 509, and the other end of the ninth switch valve pipe segment two is connected to the first inertia loading guide hydraulic cylinder B pipe segment, which is connected to the second oil port of the first inertia loading guide hydraulic cylinder 301. In the embodiments of the present application, by connecting the ninth switch valve 509 with the first oil port and the second oil port of the first inertia loading guide hydraulic cylinder 301, the two cavities of the first inertia loading guide hydraulic cylinder 301 can be directly connected to each other.

[0058] In some embodiments, the first inertia loading motor 401 is connected between the first inertia loading guide hydraulic cylinder A pipe segment and the first inertia loading guide hydraulic cylinder B pipe segment, thereby being connected with two oil chambers of the first inertia loading guide hydraulic cylinder 301, that is, the first inertia loading motor 401 is connected in parallel with the ninth switch valve 509 between the first oil port and the second oil port of the first inertia loading guide hydraulic cylinder 301.

[0059] In some embodiments, the second inertia loading guide hydraulic cylinder 302 comprises an A chamber and a B chamber, and the A chamber has a first oil port and the B chamber has a second oil port. The main pressure oil pipe further comprises a tenth switch valve pipe segment one 5009 and a tenth switch valve pipe segment two 5010, a second inertia loading guide hydraulic cylinder A pipe segment 5011, and a second inertia loading guide hydraulic cylinder B pipe segment 5012. One end of the tenth switch valve pipe segment one is connected with the tenth switch valve 510, and the other end of the tenth switch valve pipe segment one is connected with the second inertia loading guide hydraulic cylinder A pipe segment, which is connected with the first oil port of the second inertia loading guide hydraulic cylinder 302. One end of the tenth switch valve pipe segment two is connected with the ninth switch valve 509, and the other end of the tenth switch valve pipe segment two is connected with the second inertia loading guide hydraulic cylinder B pipe segment, which is connected with the second oil port of the second inertia loading guide hydraulic cylinder 302. In the embodiments of the present application, the first oil port and the second oil port of the second inertia loading guide hydraulic cylinder 302 are directly connected with each other through the tenth switch valve 510.

[0060] In some embodiments, the second inertia loading motor 402 is connected between the second inertia loading guide hydraulic cylinder A pipe segment and the second inertia loading guide hydraulic cylinder B pipe segment, thereby being connected with two oil chambers of the second inertia loading guide hydraulic cylinder 302, that is, the second inertia loading motor 402 is connected in parallel with the tenth switch valve 510 between the first oil port and the second oil port of the second inertia loading guide hydraulic cylinder 302.

[0061] In the embodiments of the present application, the first oil port and the second oil port of the first inertia loading guide hydraulic cylinder are directly connected with each other through the ninth switch valve, and the first oil port and the second oil port of the second inertia loading guide hydraulic cylinder are directly connected with each other through the tenth switch valve, so that the first inertia loading guide hydraulic cylinder and the second inertia loading guide hydraulic cylinder can lose inertia force without unloading the inertia wheels of the first inertia loading motor and the second inertia loading motor, thereby enhancing controllability and safety.

[0062] In some embodiments, the plurality of switch valves are ball valves. In some embodiments, the switch valves are electrically controlled switch valves. In embodiments of the present application, the plurality of switch valves are ball valves, which are simple in structure, reliable in control, and capable of meeting the requirements of high pressure and large flow.

[0063] In some embodiments, the first reversing valve 201 and the second reversing valve 202 are three-position four-way electromagnetic reversing valves. In some embodiments, the first reversing valve 201 and the second reversing valve 202 are servo reversing valves. In embodiments of the present application, through the servo reversing valve, the flow control and pressure control of the high-pressure large-flow hydraulic system can be controlled. In embodiments of the present application, through the servo reversing valve, the pressure, flow and direction can be accurately controlled, thereby ensuring the accuracy and real-time performance of load simulation.

[0064] In embodiments of the present application, only two reversing valves, i.e., the first reversing valve 201 and the second reversing valve 202, are provided in the entire hydraulic system, so that the plurality of working modes of the hydraulic system and the switching of the hydraulic circuit can be realized.

[0065] In some embodiments, the first inertia loading motor 401 and the second inertia loading motor 402 are bidirectional vane pumps. In embodiments of the present application, the bidirectional vane pump is used, so that the bidirectional passive loading of the first inertia loading guide hydraulic cylinder 301 and the second inertia loading guide hydraulic cylinder 302 can be realized, thereby adapting to the bidirectional movement of the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102. The bidirectional vane pump provides the inertia force for the inertia loading guide hydraulic cylinder. When the movement direction of the first inertia loading guide hydraulic cylinder and the second inertia loading guide hydraulic cylinder is changed, the rotation direction of the first inertia loading motor and the second inertia loading motor remains unchanged under the action of the inertia wheel, thereby providing resistance opposite to the movement direction, and realizing the effect of simulating the real inertia force.

[0066] In some embodiments, two pilot-controlled electric overflow 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-controlled electric overflow valves 703 and 704 are connected between the first oil port and the second oil port of the second bidirectional hydraulic cylinder 102.

[0067] In embodiments of the present application, the two pilot-controlled electric overflow valves 701 and 702 connected between the first oil port and the second oil port of the first bidirectional hydraulic cylinder 101 are connected in parallel and in opposite directions. The two pilot-controlled electric overflow valves 701 and 702 can realize safety control in two directions. The use of the pilot-controlled electric overflow valve makes the control more efficient, and remote control can be realized. When the pressure is lower than the preset threshold value, remote conduction can also be realized, thereby meeting the use requirements of special application scenarios.

[0068] In the embodiments of the present application, the two pilot-operated electric control overflow valves 703 and 704 connected between the first oil port and the second oil port of the second bidirectional hydraulic cylinder 102 are connected in parallel and in opposite directions. The two pilot-operated electric control overflow valves 703 and 704 can realize safety control in two directions, and the use of pilot-operated electric control overflow valves can realize more efficient control, remote control, and remote conduction when the pressure is lower than the preset threshold pressure when needed, thereby meeting the use requirements of special application scenarios.

[0069] In some embodiments, the overflow valve also has the function of pressure stabilization. The threshold pressure of the overflow valve can be set as the target pressure of the bidirectional hydraulic cylinder, and the output pressure of the reversing valve can be adjusted to be greater than the target pressure. Under the action of the overflow valve, the input pressure of the bidirectional hydraulic cylinder can be maintained at the target pressure.

[0070] In some embodiments, two overflow valves 801 and 802 are connected between the first oil port and the second oil port of the first inertia loading guide hydraulic cylinder 301. Two overflow valves 803 and 804 are connected between the first oil port and the second oil port of the second inertia loading guide hydraulic cylinder 302. In the embodiments of the present application, the two overflow valves 801 and 802 connected between the first oil port and the second oil port of the first inertia loading guide hydraulic cylinder 301 are connected in parallel and in opposite directions. The two overflow valves can realize safety control in two directions. The two overflow valves 803 and 804 connected between the first oil port and the second oil port of the second inertia loading guide hydraulic cylinder 302 are connected in parallel and in opposite directions. The two overflow valves can realize safety control in two directions to prevent system damage caused by excessive speed of the inertia wheel.

[0071] In some embodiments, the hydraulic system further comprises a plurality of 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 oil port of the first bidirectional hydraulic cylinder 101, the second bidirectional hydraulic cylinder 102, the first inertia loading guide hydraulic cylinder 301, and the second inertia loading guide hydraulic cylinder 302 is connected to a pressure sensor.

[0072] In some embodiments, specifically, the first pressure sensor 601 is connected to the first oil port of the first bidirectional hydraulic cylinder 101, and the second pressure sensor 602 is connected to the second oil port of the first bidirectional hydraulic cylinder 101.

[0073] 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.

[0074] 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.

[0075] 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.

[0076] In the embodiments of this application, the working pressure of each oil chamber is detected by multiple pressure sensors.

[0077] 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.

[0078] 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.

[0079] 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.

[0080] 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.

[0081] As Figure 5 shown, specifically, in some embodiments, the high-pressure large-flow inertial load hydraulic test bench 1000 includes a driving 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 hydraulic system 2000 described above. Specifically, the inertial force load simulation system is arranged between the driving system and the load simulation system, and is used to simulate the inertial force received by the driving system. The load simulation system 1002 is used to simulate the load received by the measured object in the actual environment, and test the performance of the measured object under the actual working condition. The inertial force load simulation system 1003 is used to simulate different inertial forces applied to the measured object, and is used to test the performance and stability of the measured object under dynamic working conditions such as starting, stopping and reversing, as well as the reliability under repeated inertial impact loads. The driving system 1001 includes a driving hydraulic cylinder. The inertial force load simulation system 1003 includes the first inertial load guide hydraulic cylinder 301, the second inertial load guide hydraulic cylinder 302, the first inertial load motor 401, and the second inertial load motor 402 in any of the embodiments described above. The load simulation system 1002 includes the first bidirectional hydraulic cylinder 101, the second bidirectional hydraulic cylinder 102, the first reversing valve 201, and the second reversing valve 202 in any of the embodiments described above.

[0082] With reference to Figure 6 , in the embodiments of the present application, the first bidirectional hydraulic cylinder 101 is connected with the first inertial load guide hydraulic cylinder 301, the second bidirectional hydraulic cylinder 102 is connected with the second inertial load guide hydraulic cylinder 302, and the first inertial load motor 401 and the second inertial load motor 402 are respectively connected with the first inertial load guide hydraulic cylinder 301 and the second inertial load guide hydraulic cylinder 302. In the embodiments of the present application, the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder are simultaneously connected with one driving system. Specifically, the driving system includes a driving hydraulic cylinder. The first inertial load motor 401 and the second inertial load motor 402 can be respectively connected with the first inertial wheel 4011 and the second inertial wheel 4021. In the embodiments of the present application, the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder are arranged in parallel and side by side, and can work in parallel or in series, which can meet the needs of driving load simulation of high-pressure large-flow driving system.

[0083] In some embodiments, the load simulation system 1002 of the high-pressure and high-flow inertial load hydraulic test bench specifically 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 a plurality of on-off valves. The plurality of on-off valves includes a first on-off valve, a second on-off valve, a third on-off valve, a fourth on-off valve, a fifth on-off valve, a sixth on-off valve, a seventh on-off valve, an eighth on-off valve, a ninth on-off valve, and a tenth on-off valve. When the corresponding on-off valves are controlled to be in communication so that the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 are in series working mode, the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 can simultaneously load test the drive system, and the moving direction of the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 can be switched by the first reversing valve 201. The series working of the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 can meet the needs of the drive load simulation of the high-pressure and high-load drive system 1001.

[0084] In some embodiments, when the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 are in series working mode, the ninth on-off valve and the tenth on-off valve can be independently opened or closed. For example, in the state that the ninth on-off valve is closed and the tenth on-off valve is opened, the first inertial load motor 401 is connected to the first inertial wheel 4011 to simulate the inertial force, and the second inertial load motor 402 does not provide the inertial force. In some embodiments, the ninth on-off valve and the tenth on-off valve can be alternately closed and opened, so that the first inertial load motor 401 and the second inertial load motor 402 alternately simulate the inertial force. In some embodiments, the ninth on-off valve and the tenth on-off valve can be simultaneously closed, so that the first inertial load motor 401 and the second inertial load motor 402 work together to simulate the inertial force. In some embodiments, the mass of the first inertial wheel 4011 and the second inertial wheel 4021 can be different, so as to simulate the mass mutation of the load. In the embodiments of the present application, the mass of the first inertial wheel 4011 and the second inertial wheel 4021 can be changed while the first bidirectional hydraulic cylinder 101 and the second bidirectional hydraulic cylinder 102 are continuously loaded, or the communication state of the ninth on-off valve and the tenth on-off valve can be changed, so as to simulate different inertial force conditions.

[0085] In some embodiments, specifically, the first and second bidirectional hydraulic cylinders are arranged in parallel side by side, and can be connected in parallel and work independently, to meet the driving load simulation of a large flow driving system, and the first and second bidirectional hydraulic cylinders can be alternately cycled to meet the stable and constant load demand. In some embodiments, the first bidirectional hydraulic cylinder can also be used for fixed pressure loading to simulate constant and stable fixed load loading, and the second bidirectional hydraulic cylinder can be used for dynamic pressure loading to simulate random and dynamic variable load loading. In the embodiments of the application, the high-pressure and large-flow inertial load hydraulic test bench can meet the accurate, stable and multiple demand simulation of load and inertia force, has high safety, strong adaptability and convenient operation.

[0086] In some embodiments of the application, a high-pressure and large-flow inertial load hydraulic test method is provided. The test method uses the high-pressure and large-flow inertial load hydraulic test bench in any of the above embodiments.

[0087] In some embodiments, the high-pressure and large-flow inertial load hydraulic test bench includes a first bidirectional hydraulic cylinder, a second bidirectional hydraulic cylinder and a plurality of on-off valves. The plurality of on-off valves includes a first on-off valve, a second on-off valve, a third on-off valve, a fourth on-off valve, a fifth on-off valve, a sixth on-off valve, a seventh on-off valve, an eighth on-off valve, a ninth on-off valve and a tenth on-off valve. The test method includes: the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder are connected to one driving system at the same time, and the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder work in a series working mode, or work in a parallel working mode, or switch between the series working mode and the parallel working mode.

[0088] In some embodiments, in the series working mode, the ninth on-off valve is closed, the tenth on-off valve is connected, a first inertia wheel is connected to the first inertia loading motor to simulate inertia force, and the second inertia loading motor does not provide inertia force.

[0089] In some embodiments, in the series working mode, the ninth on-off valve is connected, the tenth on-off valve is closed, a second inertia wheel is connected to the second inertia loading motor to simulate inertia force, and the first inertia loading motor does not provide inertia force.

[0090] In some embodiments, in the series working mode, the ninth on-off valve is connected, the tenth on-off valve is closed, a second inertia wheel is connected to the second inertia loading motor to simulate inertia force, and the first inertia loading motor does not provide inertia force.

[0091] In some embodiments, the first inertia wheel and the second inertia wheel have different masses, the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder are in the series working mode, the ninth switch valve is kept closed and the tenth switch valve is connected in a first time period; then the tenth switch valve is closed in a second time period, so as to simulate the inertia force of the load mass mutation. The second time period is continuous with the first time period, that is, the starting time of the second time period is the same as the ending time of the first time period.

[0092] In some embodiments, the first inertia wheel is replaced in the time period when the ninth switch valve is connected, so as to change the mass of the first inertia wheel; in some embodiments, the second inertia wheel is replaced in the time period when the tenth switch valve is connected, so as to change the mass of the second inertia wheel. In the embodiments of the present application, the corresponding inertia wheel can be replaced in the time period when the ninth switch valve or the tenth switch valve is connected, so as to simulate different load mass inertia forces in the state that the test bench does not stop.

[0093] In some embodiments, the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder are in the parallel working mode, the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder are simultaneously connected to a driving system, and the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder are alternately and cyclically loaded. In the embodiments of the present application, by controlling the first reversing valve and the second reversing valve, the loading switching period, size and direction of the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder are adjusted, so as to realize accurate simulation of the load and meet the stable and constant loading demand.

[0094] In some embodiments, the first bidirectional hydraulic cylinder is used for fixed pressure loading to simulate constant and stable fixed load loading, and the second bidirectional hydraulic cylinder is used for dynamic pressure loading to simulate random and dynamic change load loading. In the embodiments of the present application, by controlling the first reversing valve and the second reversing valve, the loading pressure size and direction of the first bidirectional hydraulic cylinder and the second bidirectional hydraulic cylinder are adjusted, so as to realize accurate simulation of the load. In the test process, the amplitude and period of the dynamic loading can be adjusted according to the actual demand, so that the test working condition is closer to the real running environment, and the simulation precision and application range of the test bench are improved.

[0095] It can be understood that, in the embodiments of the present application, similar to the series working mode, the first inertia loading motor and the second inertia loading motor can also be controlled by the ninth switch valve and the tenth switch valve to perform corresponding inertia force simulation in the parallel working mode.

[0096] Reference Figure 7In some embodiments, the corresponding switch valve can also be controlled to connect the first and second bidirectional hydraulic cylinders 101 and 102, so that the first and second drive systems 1011 and 1021 can be subjected to load testing when the first and second bidirectional hydraulic cylinders 101 and 102 are in parallel working mode, and the moving direction of the first and second bidirectional hydraulic cylinders 101 and 102 can be controlled by the first and second reversing valves 201 and 202, respectively.

[0097] In some embodiments, the inertia load simulation system 1003 of the high-pressure and large-flow inertia load hydraulic test bench includes a first inertia load guide hydraulic cylinder 301, a second inertia load guide hydraulic cylinder 302, a first inertia load motor 401, and a second inertia load motor 402. The first inertia load guide hydraulic cylinder is controlled by the first inertia load motor 401 to generate a first target inertia load acting on the first measured object to measure the performance and reliability of the first measured object. The second inertia load guide hydraulic cylinder is controlled by the second inertia load motor 402 to generate a second target inertia load acting on the second measured object to measure the performance and reliability of the second measured object. The first and second target inertias are determined by the test scenario and can be periodic inertias, such as the inertia acting on the measured object when simulating start-stop. The inertia load guide hydraulic cylinder needs to generate a corresponding load when it is periodically started and stopped, such as when testing reliability, the inertia load guide hydraulic cylinder needs to simulate a periodic or continuous load change. This periodic or continuous load change can be achieved by controlling the inertia load motor. The first and second inertia load guide hydraulic cylinders 301 and 302 can meet the needs of high-pressure and large-flow drive load simulation of the drive system 1001.

[0098] In some embodiments of the present application, a high-pressure and large-flow inertia load hydraulic test method is also provided. The test method uses the high-pressure and large-flow inertia load hydraulic test bench in any of the above embodiments. In some embodiments, the high-pressure and large-flow inertia load hydraulic test bench includes a first bidirectional hydraulic cylinder, a second bidirectional hydraulic cylinder, and a plurality of switch valves. The plurality of switch valves includes a first switch valve, a second switch valve, a third switch valve, a fourth switch valve, a fifth switch valve, a sixth switch valve, a seventh switch valve, an eighth switch valve, a ninth switch valve, and a tenth switch valve. The test method includes connecting a first bidirectional hydraulic cylinder and a second bidirectional hydraulic cylinder to a first drive system and a second drive system, respectively.

[0099] In the embodiments of the present 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, and the first and second bidirectional hydraulic cylinders work in parallel working mode to perform comparative tests on the first and second drive systems.

[0100] In some embodiments, the high pressure high flow inertial load hydraulic test bench can be used for simulation of a marine power system. The drive system 1001 can be a power system of a marine vessel. In some embodiments, the high pressure high flow inertial load hydraulic test bench can be used for simulation of a hatch power system of a marine vessel. The drive system 1001 can be a hydraulic actuator of a hatch of a marine vessel.

[0101] Those skilled in the art can easily understand that the above description is only the preferred embodiment of the present application, and is not used to limit the present application, and any modification, equivalent replacement and improvement made within the spirit and principle of the present application should be included in the protection scope of the present application.

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; 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. 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.

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 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 inertial wheel and the second inertial wheel have different masses.

7. The hydraulic system according to claim 6, characterized in that, Two pilot-operated electrically controlled relief valves with opposite directions are connected in parallel between the first oil port and the second oil port of the first bidirectional hydraulic cylinder. The second bidirectional hydraulic cylinder has two pilot-operated electrically controlled relief valves connected in parallel between its first and second oil ports.

8. The hydraulic system according to claim 7, 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.

9. 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 1-8; 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.

10. 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 9, 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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