A high-speed hydraulic pump and multi-way valve test bench for engineering machinery

Abstract

The application discloses a kind of test test bench of high-speed hydraulic pump and multi-way valve for engineering machinery, comprising: main oil tank, oil suction and oil return assembly, hydraulic component performance test assembly, collect oil assembly of collecting hydraulic component external leakage hydraulic oil, hydraulic oil temperature control assembly, pilot control assembly;Hydraulic component performance test assembly is realized load-sensitive, open or closed hydraulic component forward or reverse rotation pressure and flow test by load-sensitive port valve group, control reversing valve group, loading valve group, oil supplement valve group;In pilot control assembly, the hydraulic oil of main oil tank is pumped to high-pressure plate filter, and after being shunted to multiple groups of different parameters proportional pressure-reducing valve and three-position four-way reversing valve, it flows into pilot control port.The application can integrally complete high-speed hydraulic pump, multi-way valve multi-working condition comprehensive detection, adapt various types of hydraulic components, integrate multi-working condition oil suction, leakage grading detection, pressure flow, adaptive oil temperature regulation and control, pilot oil supply, oil collection recovery function.

Description

Technical Field

[0001] This invention relates to the field of hydraulic engineering machinery, and in particular to a test bench for a high-speed hydraulic pump and multi-way valve for engineering machinery. Background Technology

[0002] As the core component of a hydraulic system, the performance of hydraulic components directly determines the operational stability, reliability, and efficiency of the entire hydraulic system. They are widely used in various fields such as machinery manufacturing and aerospace. Therefore, comprehensive performance testing of hydraulic components has significant engineering importance and practical application value.

[0003] Currently, the field of hydraulic component testing faces numerous technical bottlenecks. Existing testing equipment is mostly designed for single functions, typically only capable of testing one or a few performance parameters of hydraulic components. It cannot achieve integrated testing of multiple functions such as oil suction, leakage, pressure and flow, oil replenishment, and oil temperature control. Its testing range is limited and its compatibility is poor, making it difficult to adapt to the testing needs of different types of hydraulic components, including open, closed, and load-sensitive components. Furthermore, existing testing equipment suffers from insufficient parameter acquisition accuracy during testing, failing to comprehensively monitor key parameters such as pressure, flow, speed, and torque under different operating conditions. It also lacks comprehensive auxiliary functions, such as oil recovery during testing, adaptive hydraulic oil temperature adjustment, and pilot control. This results in cumbersome testing procedures, a large amount of manual operation, and low testing efficiency, making it difficult to meet the high-precision, comprehensive testing requirements of modern hydraulic components.

[0004] Furthermore, existing testing technologies lack mature, integrated solutions for scenarios such as forward and reverse rotation testing of different types of hydraulic components, graded detection of different leakage amounts, and precise control under different oil suction conditions (atmospheric pressure, boosted pressure, negative pressure). This often necessitates the construction of multiple independent testing platforms, increasing testing costs and leading to inconsistent test data and operational complexity. With the continuous development of hydraulic technology, the structure and function of hydraulic components are becoming increasingly complex, placing higher demands on the comprehensive performance of testing systems. There is an urgent need for a hydraulic component testing system capable of integrated testing of multiple types, operating conditions, and parameters, with comprehensive auxiliary functions. This system would address the shortcomings of existing technologies, improve testing efficiency and accuracy, and provide reliable support for the performance verification of hydraulic components. Summary of the Invention

[0005] To address the shortcomings of existing technologies, this invention proposes a test bench for high-speed hydraulic pumps and multi-way valves used in engineering machinery, which meets the industry's demand for integrated testing of multiple types, multiple working conditions, and multiple parameters.

[0006] The specific technical solution is as follows: A test bench for a high-speed hydraulic pump and multi-way valve for engineering machinery includes: a main oil tank, an oil suction and return assembly, a hydraulic component performance testing assembly, an oil collection assembly, a hydraulic oil temperature control assembly, and a pilot control assembly. The oil suction and return assembly includes a normal pressure oil suction circuit, a booster oil suction circuit, and a negative pressure oil suction circuit, which are respectively connected to the two oil suction ports of the hydraulic element and the main oil tank. The oil circuit switching is controlled by the valve body. It also includes two return oil circuits with different ranges, which are respectively connected to the two oil return ports of the hydraulic element and the main oil tank. The hydraulic component performance testing assembly uses a load-sensitive P-port valve group, an Ls-port valve group, a control directional valve group, and a loading valve group to test the pressure and flow of load-sensitive hydraulic components. It also uses the control directional valve group and the loading valve group to test the pressure and flow of open hydraulic components during forward or reverse rotation, and uses the control directional valve group, the loading valve group, and the replenishing valve group to test the pressure and flow of closed hydraulic components during forward or reverse rotation. The P1 port of the control directional valve group is connected to the P port of the loading valve group. The T port of the loading valve group is connected to a three-way ball valve through a brazed plate radiator. One output of the three-way ball valve is connected to the main oil tank, and the other output is connected to the T1 port of the replenishing valve group. The replenishing valve group works in conjunction with the control directional valve group to return hydraulic oil to the hydraulic components. In the oil collection assembly, the leaked hydraulic oil from the hydraulic components flows into the main oil tank in sequence through the recovery oil tank, the suction filter, the leakage recovery pump set, and the pipeline filter. In the hydraulic oil temperature control component, the hydraulic oil in the main oil tank flows back to the main oil tank after passing through the valve body, circulating pump group, pipeline filter, brazed plate radiator, and check valve in sequence; the brazed plate radiator is connected to the cooling water through the valve body to achieve hydraulic oil cooling, and the sheathed tubular oil heater installed on the main oil tank is used to achieve hydraulic oil heating. In the pilot control assembly, the hydraulic oil in the main oil tank passes sequentially through a ball valve, an external control pump group, a check valve, and a high-pressure plate filter, and then is diverted to multiple sets of proportional pressure reducing valves and three-position four-way directional valves with different parameters, and flows into the corresponding pilot control port under control.

[0007] Furthermore, the control directional valve assembly comprises four units: the first unit includes a 2-way cartridge valve three, a 2-way cartridge valve cover plate five, and a two-position three-way shut-off directional valve one; the second unit includes a 2-way cartridge valve four, a 2-way cartridge valve cover plate six, and a two-position three-way shut-off directional valve two; the third unit includes a 2-way cartridge valve five, a 2-way cartridge valve cover plate seven, and a two-position three-way shut-off directional valve three; and the fourth unit includes a 2-way cartridge valve six, a 2-way cartridge valve cover plate eight, and a two-position three-way shut-off directional valve four. In the de-energized state, ports B and C of the four two-position three-way shut-off directional valves are open; in the energized state, ports A and C are open. Ports A and B of each unit's two-position three-way shut-off directional valve are connected to the main oil circuit of the two-way cartridge valve, and port C is connected to the cover plate of the two-way cartridge valve. Port B of two-position three-way shut-off directional valve one and two-position three-way shut-off directional valve four is connected to port A of the control directional valve group; port B of two-position three-way shut-off directional valve two and two-position three-way shut-off directional valve three is connected to port B of the control directional valve group; port A of two-position three-way shut-off directional valve one and two-position three-way shut-off directional valve two is connected to port P of the control directional valve group; port A of two-position three-way shut-off directional valve three and two-position three-way shut-off directional valve four is connected to port P1 of the control directional valve group.

[0008] Furthermore, the loading valve assembly includes two oil circuits from port P to port T. The first oil circuit is equipped with a valve assembly consisting of a directional two-way cartridge valve, a two-way cartridge valve cover plate, and a solenoid ball valve, as well as a two-way cartridge proportional throttle valve. The second oil circuit is equipped with a valve assembly consisting of a solenoid ball valve, a proportional relief valve, a direct-acting relief valve, a pressure two-way cartridge valve, and a two-way cartridge valve cover plate. If the solenoid ball valve is energized, pressurized oil flows into the first oil circuit and simulates a load by controlling the two-way cartridge proportional throttle valve. If it is de-energized, pressurized oil flows into the second oil circuit and simulates a load by controlling the set pressure of the proportional relief valve.

[0009] Furthermore, in the hydraulic component performance testing assembly, the hydraulic component rotates under the control of a high-speed motor. Port A of the hydraulic component is connected to three oil circuits: one circuit connects to the load-sensitive P-port via a load-sensitive P-port valve group, which includes a directional two-way cartridge valve, a two-way cartridge proportional throttle valve, and a two-way cartridge valve cover; the second circuit connects to the Ls-port via an Ls-port valve group, which includes a solenoid ball valve; the third circuit connects to Port A of the control directional valve group via a high-pressure filter and a screw flow meter; and Port B of the hydraulic component connects to Port B of the control directional valve group via a high-pressure filter and a screw flow meter.

[0010] Furthermore, a directional two-way cartridge valve and a two-way cartridge valve cover plate are installed on the oil line connecting the T1 port and P1 port of the replenishing valve group. The P port of the replenishing valve group is connected to the main oil tank through a replenishing pump group composed of a hydraulic pump and a variable frequency motor, and a thin ball valve. The P port of the replenishing valve group is output from the S port to the replenishing port of the hydraulic component after passing through a high-pressure plate filter. The oil line between the high-pressure plate filter and the S port of the replenishing valve group is connected to the P1 port of the replenishing valve group through a valve group composed of a directional two-way cartridge valve, a two-way cartridge valve cover plate, and a two-position three-way shut-off directional valve. The oil line between the high-pressure plate filter and the S port of the replenishing valve group is connected to the T port of the replenishing valve group through a valve group composed of a pressure two-way cartridge valve, a two-way cartridge valve cover plate, and a proportional relief valve.

[0011] Furthermore, in the oil suction and return assembly, the oil suction port 1 of the hydraulic component is connected to the main oil tank in sequence through ball valve 1, booster pump group, and thin ball valve 1; the oil suction port 2 is connected to the main oil tank in sequence through ball valve 2 and thin ball valve 2; the oil passage between ball valve 1 and booster pump group is connected to the oil passage between ball valve 2 and thin ball valve 2 through ball valve 3; the oil passage between ball valve 1 and booster pump group is also connected to the main oil tank through booster valve group; the booster valve group includes a pressure two-way cartridge valve 1, a two-way cartridge valve cover plate 1, and a proportional relief valve 1; In the oil suction and return assembly, the return port 1 of the hydraulic component is connected to the main oil tank in sequence through pipeline filter one, gear flow meter, and check valve two, and the return port 2 is connected to the main oil tank in sequence through pipeline filter three, screw flow meter one, and check valve one.

[0012] Furthermore, the pilot control assembly includes four pilot control ports, each corresponding to a three-position four-way directional valve, and is equipped with a pressure transmitter to measure the hydraulic oil pressure. The main oil tank is connected to the P port of the external control valve group via a three-way ball valve, an external control pump group, a check valve, and the external control valve group in sequence. The P port is connected to the A1 and B1 ports of the external control valve group via a high-pressure plate filter and a three-position four-way directional valve one, and is connected to the pilot control port 1. The oil circuit between the P port of the external control valve group and the high-pressure plate filter is connected to a hydraulic bladder accumulator arranged outside the external control valve group. The P port of the external control valve group is connected to the A2 and B2 ports of the external control valve group in sequence via a proportional pressure reducing valve one and a three-position four-way directional valve two, and is connected to the pilot control port 2. The P port of the external control valve group is connected to the A3 and B3 ports of the external control valve group in sequence via a proportional pressure reducing valve two and a three-position four-way directional valve three, and is connected to the pilot control port 3. The P port of the external control valve group is connected to the A4 and B4 ports of the external control valve group in sequence via a proportional pressure reducing valve three and a three-position four-way directional valve four, and is connected to the pilot control port 4.

[0013] Furthermore, during the pressure and flow test of the load-sensitive hydraulic component, the oil inlet of the load-sensitive hydraulic component draws oil through the oil inlet and outlet assembly. The hydraulic oil from the outlet of the load-sensitive hydraulic component passes through the load-sensitive P-port valve group, high-pressure filter one, and screw flow meter two to reach the control directional valve group. At this time, the two-position three-way shut-off directional valve three and two-position three-way shut-off directional valve four in the control directional valve group are energized, and the hydraulic oil enters the loading valve group through the two-way cartridge valve six and the two-way cartridge valve cover plate eight. The hydraulic oil exceeding the set pressure of the relief valve is output from the T port of the loading valve group and flows back to the main oil tank. At the same time, the hydraulic oil from the outlet reaches the Ls port of the hydraulic component through the solenoid ball valve. The pressure at each point is measured by a pressure gauge, a high-frequency pressure sensor, and a pressure transmitter, and the flow rate is measured by the screw flow meter.

[0014] The beneficial effects of this invention are: (1) This invention addresses the shortcomings of existing testing equipment, such as limited functionality and poor compatibility. It can perform integrated testing of high-speed hydraulic pumps and multi-way valves under multiple operating conditions. It is compatible with open, closed, and load-sensitive component testing. The equipment integrates a full set of auxiliary functions, including oil suction, leakage classification detection, pressure and flow rate control, adaptive oil temperature control, pilot oil supply, and oil collection and recovery. It supports forward and reverse rotation of pump components and precise control of various oil suction conditions, such as normal pressure, boost pressure, and negative pressure.

[0015] (2) The present invention can realize multi-channel high-precision synchronous acquisition of key parameters such as speed, torque, pressure and flow rate, without the need to build multiple separate platforms, thus reducing equipment investment costs.

[0016] (3) The automated process of the present invention reduces manual operation, has high consistency of test data, takes into account both high-precision R&D testing and batch quality inspection, comprehensively improves test accuracy and efficiency, and provides reliable test support for the performance verification and optimization iteration of hydraulic components of engineering machinery. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the test bench for high-speed hydraulic pumps and multi-way valves used in engineering machinery, as described in this embodiment of the invention.

[0018] Figure 2 This is a schematic diagram illustrating the testing principle of the hydraulic component's oil suction and leakage functions in an embodiment of the present invention.

[0019] Figure 3 This is a schematic diagram illustrating the testing principle of load-sensitive and open / closed hydraulic components in an embodiment of the present invention.

[0020] Figure 4 This is a schematic diagram illustrating the principle of the oil collection and hydraulic oil temperature control functions in an embodiment of the present invention.

[0021] Figure 5 This is a schematic diagram illustrating the principle of the pilot control function in an embodiment of the present invention.

[0022] In the diagram, the following components are included: 1. Main oil tank; 2. Socket-type resistance thermometer; 3. Level transmitter; 4. Moisture-absorbing air filter; 5. Sheathed tubular oil heater; 6. Low-pressure ball valve; 7. Level / temperature gauge; 8-1 and 8-2 thin ball valves; 9. Screw pump; 10. Variable frequency motor; 11. Two-way cartridge valve; 12. Two-way cartridge valve cover; 13-1 and 13-2 proportional relief valves; 14-1, 14-2, 14-3, 14-4, 14-5, and 14-6 pressure gauges; 15-1 and 15-2 pressure transmitters; 16-1, 16-2, and 16-3 ball valves; 17. Check valve; 3. Pressure transmitter. 18-1, Pressure Transmitter IV; 18-2, Pipeline Filter I; 19-1, Pipeline Filter II; 19-2, Pipeline Filter III; 20, Gear Flow Meter; 21, Screw Flow Meter I; 22, Check Valve II; 23, Two-Way Cartridge Valve I; 24-1, Two-Way Cartridge Valve II; 24-2, Two-Way Cartridge Valve III; 24-3, Two-Way Cartridge Valve IV; 24-4, Two-Way Cartridge Valve V; 24-5, Two-Way Cartridge Valve VI; 24-6, Two-Way Cartridge Valve VII; 24-7, Two-Way Cartridge Valve VIII; 24-8, Two-Way Cartridge Valve Cover Plate II; 25-1, Two-Way Cartridge Valve Cover Plate III; 25-2, Solenoid Ball Valve I; 26, High-Frequency Pressure Sensor I; 27-1, High-Frequency Pressure Sensor II; 27-2, Two-Way Cartridge Proportional Throttling Valve I 8-1, Two-way cartridge proportional throttle valve II 28-2; Two-way cartridge valve cover plate IV 29-1, Two-way cartridge valve cover plate V 29-2, Two-way cartridge valve cover plate VI 29-3, Two-way cartridge valve cover plate VII 29-4, Two-way cartridge valve cover plate VIII 29-5, Two-way cartridge valve cover plate IX 29-6, Two-way cartridge valve cover plate X 29-7; High-pressure filter I 30-1, High-pressure filter II 30-2; Screw flow meter II 31-1, Screw flow meter III 31-2; Solenoid ball valve II 32-1, Solenoid ball valve III 32-2; Proportional relief valve III 33, Direct-acting relief valve I 34, Pressure two-way cartridge valve II 35, High-speed motor 36, Diaphragm coupling 37, Torque tachometer 38; Two-position three-way shut-off directional valve I 39-1, Two-position three Two-way three-way shut-off directional valve II 39-2, two-position three-way shut-off directional valve III 39-3, two-position three-way shut-off directional valve IV 39-4, two-position three-way shut-off directional valve V 39-5; brazed plate radiator I 40, proportional water valve 41, three-way ball valve I 42, hydraulic pump 43, variable frequency motor II 44, high-pressure plate filter I 45; pressure transmitter V 46-1, pressure transmitter VI 46-2, pressure transmitter VII 46-3, pressure transmitter VIII 46-4, pressure transmitter IX 46-5; high-pressure ball valve 47, float level switch 48, air filter 49, liquid level and temperature gauge II 50, oil suction filter 51, vane pump I 52, three-phase asynchronous motor I 53; shockproof pressure gauge I 54-1, shockproof pressure gauge II 54-2;55. Direct-acting relief valve II; 56. Pipeline filter IV; 57. Check valve III; 58. Brazed plate radiator II; 59. Solenoid water valve; 60. Pipeline filter V; 61. Pipeline filter VI; 62. Direct-acting relief valve III; 63. Screw pump II; 64-1 and 64-2 of three-phase asynchronous motor II and III; 65-1 and 65-2 of thin ball valve III and IV; 66. Three-way ball valve II; 67. Vane pump II; 68. Check valve IV; 69. Pilot-operated proportional relief valve; 70. Hydraulic bladder accumulator; Pressure transmitter. Pressure transmitter 71-1 (11), pressure transmitter 71-2 (11), high-pressure plate filter 72, proportional pressure reducing valve 1 (1), proportional pressure reducing valve 2 (2), proportional pressure reducing valve 3 (3), three-position four-way directional valve 1 (1), three-position four-way directional valve 2 (2), three-position four-way directional valve 3 (3), three-position four-way directional valve 4 (4), solenoid directional valve 77, pressure two-way cartridge valve 3 (3), two-way cartridge valve cover plate 11 (11), pressure transmitter 80-1 (12), pressure transmitter 80-2 (13), recovery oil tank 81. Detailed Implementation

[0023] The present invention will be described in detail below with reference to the accompanying drawings and preferred embodiments. The objectives and effects of the present invention will become clearer as a result. The present 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 of the invention and are not intended to limit the invention.

[0024] A test bench for high-speed hydraulic pumps and multi-way valves for engineering machinery includes: a main oil tank 1, a socket-type resistance thermometer 2, a level transmitter 3, a moisture-absorbing air filter 4, a sheathed tubular oil heater 5, a low-pressure ball valve 6, a level and temperature gauge 7, an oil suction and return assembly, a hydraulic component performance testing assembly, an oil collection assembly, a hydraulic oil temperature control assembly, and a pilot control assembly.

[0025] like Figure 1 As shown, the main oil tank 1 is divided into a clean oil area and a dirty oil area. The main oil tank 1 is equipped with a socket-type thermal resistor 2, a level transmitter 3, a moisture-absorbing air filter 4, a sheathed tubular oil heater 5, a low-pressure ball valve 6, and a level and temperature gauge 7.

[0026] like Figure 2As shown, the oil suction and return assembly includes: a booster pump group consisting of a thin ball valve 8-1, a thin ball valve 8-2, a screw pump 9, and a variable frequency motor 10; a pressure two-way cartridge valve 11; a two-way cartridge valve cover plate 12; a proportional relief valve 13-1; a pressure gauge 14-1, a pressure gauge 2 14-2, a pressure gauge 3 14-3, a pressure gauge 4 14-4; a pressure transmitter 15-1, a pressure transmitter 2 15-2; a ball valve 16-1, a ball valve 2 16-2, a ball valve 3 16-3; a check valve 17; a pressure transmitter 3 18-1; a pressure transmitter 4 18-2; a pipeline filter 19-1; a pipeline filter 3 20; a gear flow meter 21; a screw flow meter 22; and a check valve 23. The hydraulic component's suction port 1 is connected to the main oil tank 1 via ball valve 16-1, booster pump set, and thin ball valve 8-1 in sequence. A pressure gauge 14-1 and a pressure transmitter 15-1 are installed on the oil line between ball valve 16-1 and suction port 1 to measure the pressure of the corresponding suction oil line in real time. The suction port 2 is connected to the main oil tank 1 via ball valve 2 16-2 and thin ball valve 2 8-2 in sequence. A pressure gauge 2 14-2 and a pressure transmitter 2 15-2 are installed on the oil line between ball valve 2 16-2 and suction port 2. The oil passage between ball valve 16-1 and the booster pump unit is connected through the oil passage between ball valve 3 16-3, ball valve 2 16-2, and thin ball valve 2 8-2. The oil passage between ball valve 16-1 and the booster pump unit is also connected to the main oil tank 1 through the booster valve group to ensure the oil suction pressure. The booster valve group includes a pressure two-way cartridge valve 11, a two-way cartridge valve cover plate 12, and a proportional relief valve 13-1.

[0027] The return port 1 of the hydraulic component is connected to the main oil tank 1 in sequence through pipeline filter 19-1, gear flow meter 21, and check valve 23. Pressure gauge 3 14-3 and pressure transmitter 3 18-1 are installed on the oil line between pipeline filter 19-1 and return port 1. Return port 2 is connected to the main oil tank 1 in sequence through pipeline filter 3 20, screw flow meter 22, and check valve 17. Pressure gauge 4 14-4 and pressure transmitter 4 18-2 are installed on the oil line between pipeline filter 3 20 and return port 2.

[0028] like Figure 3 As shown, the hydraulic component performance testing assembly includes: a directional two-way cartridge valve, a two-way cartridge proportional throttle valve, a pressure two-way cartridge valve, a two-way cartridge valve cover plate, a solenoid ball valve, a high-frequency pressure sensor, a high-pressure filter, a screw flow meter, a proportional relief valve 33, a direct-acting relief valve 1 34, a high-speed motor 36, a diaphragm coupling 37, a torque tachometer 38, a two-position three-way shut-off directional valve, a brazed plate radiator 1 40, a proportional water valve 41, a three-way ball valve 1 42, a hydraulic pump 43, a variable frequency motor 2 44, a high-pressure plate filter 1 45, a pressure transmitter, a high-pressure ball valve 47, a thin ball valve 4 65-2, and a solenoid directional valve 77.

[0029] The high-speed motor 36 controls the rotation of the hydraulic components through the diaphragm coupling 37, and a torque and speed meter 38 is set to synchronously measure the real-time torque and speed of the rotating shaft. An electromagnetic reversing valve 77 is set to control the rotation direction, and pressure transmitters 6 46-2 and 7 46-3 are set to measure the pressure in real time. The hydraulic component's A port is equipped with a pressure gauge 14-5 and a high-frequency pressure sensor 27-1. The hydraulic component's A port is connected to three oil circuits. One circuit is connected to the load-sensitive P port through a load-sensitive P port valve group, and a pressure transmitter 80-2 is installed on the oil circuit. The load-sensitive P port valve group includes a directional two-way cartridge valve 24-2, a two-way cartridge proportional throttle valve 28-1, and a two-way cartridge valve cover 29-1. The second circuit is connected to the Ls port through an Ls port valve group, and a pressure transmitter 80-1 is installed on the oil circuit. The Ls port valve group includes a solenoid ball valve 26. The third circuit is connected to the A port of the control directional valve group through a high-pressure filter 30-1 and a screw flow meter 31-1. The B port of the hydraulic component is connected to the B port of the control directional valve group through the high pressure filter 2 30-2 and the screw flow meter 3 31-2. A pressure gauge 6 14-6 and a high frequency pressure sensor 2 27-2 are installed on the oil line between the B port of the hydraulic component and the high pressure filter 2 30-2.

[0030] The control directional valve assembly comprises four units. The first unit includes a 2-way cartridge valve (24-3), a 2-way cartridge valve cover plate (29-2), and a two-position three-way shut-off directional valve (39-1). The second unit includes a 2-way cartridge valve (24-4), a 2-way cartridge valve cover plate (29-3), and a two-position three-way shut-off directional valve (39-2). The third unit includes a 2-way cartridge valve (24-5), a 2-way cartridge valve cover plate (29-4), and a two-position three-way shut-off directional valve (39-3). The fourth unit includes a 2-way cartridge valve (24-6), a 2-way cartridge valve cover plate (29-5), and a two-position three-way shut-off directional valve (39-4). In the de-energized state, ports B and C of the four two-position three-way shut-off directional valves are open; in the energized state, ports A and C are open. Ports A and B of each unit's two-position three-way shut-off directional valve are connected to the main oil circuit of the two-way cartridge valve, and port C is connected to the cover plate of the two-way cartridge valve. Port B of two-position three-way shut-off directional valve 1 (39-1) and two-position three-way shut-off directional valve 4 (39-4) is connected to port A of the control directional valve group; Port B of two-position three-way shut-off directional valve 2 (39-2) and two-position three-way shut-off directional valve 3 (39-3) is connected to port B of the control directional valve group; Port A of two-position three-way shut-off directional valve 1 (39-1) and two-position three-way shut-off directional valve 2 (39-2) is connected to port P of the control directional valve group; Port A of two-position three-way shut-off directional valve 3 (39-3) and two-position three-way shut-off directional valve 4 (39-4) is connected to port P1 of the control directional valve group.

[0031] The P1 port of the control directional valve group is connected to the P port (pressure inlet) of the loading valve group. Hydraulic oil flows into the loading valve group from the P port through the third or fourth unit of the control directional valve group. The T port (return port) of the loading valve group is connected to the three-way ball valve 42. A brazed plate radiator 40 is installed on this section of the oil circuit. The brazed plate radiator 40 is connected to the proportional water valve 41. One output of the three-way ball valve 42 is connected to the main oil tank 1, and the other output is connected to the T1 port of the replenishing valve group.

[0032] The loading valve assembly includes two oil circuits (from port P to port T). The first oil circuit is equipped with a valve assembly consisting of a directional two-way cartridge valve 24-1, a two-way cartridge valve cover plate 25-2, and a solenoid ball valve 32-2, as well as a two-way cartridge proportional throttle valve 28-2. The second oil circuit is equipped with a valve assembly consisting of a solenoid ball valve 22-1, a proportional relief valve 33, a direct-acting relief valve 34, a pressure two-way cartridge valve 35, and a two-way cartridge valve cover plate 25-1. When the solenoid ball valve 32-2 is energized, pressurized oil flows into the first oil circuit and simulates the load by controlling the two-way cartridge proportional throttle valve 28-2. When de-energized, pressurized oil flows into the second oil circuit and simulates the load by controlling the set pressure of the proportional relief valve 33.

[0033] The oil circuit connecting the T1 port and P1 port of the replenishing valve assembly is equipped with a directional two-way cartridge valve 7 24-7 and a two-way cartridge valve cover plate 9 29-6. The P port of the replenishing valve assembly is connected to the main oil tank 1 via a replenishing pump assembly consisting of hydraulic pump 43 and variable frequency motor 44, and thin ball valve 65-2. The P port of the replenishing valve assembly is connected to the S port of the replenishing valve assembly via high-pressure plate filter 45. The S port is connected to the replenishing port of the hydraulic component via high-pressure ball valve 47. A pressure transmitter 46-1 is installed between the P port and the high-pressure plate filter 45. The oil circuit between the high-pressure plate filter 45 and the S port of the replenishing valve assembly is connected to the P1 port of the replenishing valve assembly via a valve assembly consisting of directional two-way cartridge valve 24-8, two-way cartridge valve cover plate 29-7, and two-position three-way shut-off directional valve 39-5. The oil circuit between the high-pressure plate filter 45 and the S port of the replenishing valve assembly is connected to the T port of the replenishing valve assembly via a valve assembly consisting of pressure two-way cartridge valve 78, two-way cartridge valve cover plate 79, and proportional relief valve 13-2.

[0034] The P1 port of the replenishing valve group is connected to the P port of the control directional valve group. When the hydraulic component is closed and the battery ball valve 39-2 is energized, the hydraulic oil output by the replenishing valve group returns to the closed hydraulic component through the first or second unit of the control directional valve group, the screw flow meter, and the high-pressure filter to replenish the oil.

[0035] like Figure 4As shown, the oil collection assembly includes: a pipeline filter 19-2, a float level switch 48, an air filter 49, a level and temperature gauge 50, a suction filter 51, a vane pump 52, a three-phase asynchronous motor 53 forming an oil recovery pump group, a shockproof pressure gauge 54-1, a direct-acting relief valve 55, a pipeline filter 56, and a recovery tank 81. The recovery tank 81, used to collect leaked hydraulic oil from hydraulic components, is equipped with a float level switch 48, an air filter 49, a level and temperature gauge 50, and a suction filter 51. The output port of the suction filter 51 is connected to the main oil tank 1 through the oil recovery pump group, pipeline filter 19-2, and pipeline filter 56. A shockproof pressure gauge 54-1 is installed on the oil line between the oil recovery pump group and the pipeline filter 19-2, and a direct-acting relief valve 55 is installed on this section of the oil line and connected to the main oil tank 1.

[0036] The hydraulic oil temperature control assembly includes: a sheathed tubular heater 5, a shockproof pressure gauge 2 54-2, a check valve 3 57, a brazed plate radiator 2 58, a solenoid water valve 59, a pipeline filter 5 60, a pipeline filter 6 61, a direct-acting relief valve 3 62, a circulating pump assembly consisting of a screw pump 2 63 and a three-phase asynchronous motor 2 64-1, and a thin ball valve 3 65-1. The hydraulic oil in the main oil tank 1 flows back to the main oil tank 1 after passing sequentially through the thin ball valve 3 65-1, the circulating pump assembly, the pipeline filter 6 61, the pipeline filter 5 60, the brazed plate radiator 2 58, and the check valve 3 57. The oil circuit between the circulating pump set and the pipeline filter 61, and the oil circuit between the brazed plate radiator 2 58 and the one-way valve 3 57 are connected through the direct-acting relief valve 3 62. A shockproof pressure gauge 2 54-2 is installed on the oil circuit between the circulating pump set and the pipeline filter 61. The brazed plate radiator 2 58 is connected to the cooling water through the solenoid water valve 59. By controlling the energization and de-energization of the solenoid water valve 59, the flow of cooling water into the brazed plate radiator 2 58 is controlled, thereby realizing the cooling control of the hydraulic oil. The heating control of the hydraulic oil is realized by controlling the sheathed tubular oil heater 5 installed on the main oil tank 1.

[0037] like Figure 5 As shown, the pilot control assembly includes: a pressure transmitter, an externally controlled pump group consisting of a three-phase asynchronous motor (64-2) and a vane pump (67), a three-way ball valve (66), a check valve (68), a pilot-operated proportional relief valve (69), a hydraulic bladder accumulator (70), a high-pressure plate filter (72), a proportional pressure reducing valve, and a three-position four-way directional valve. The pilot control assembly has four pilot control ports, each corresponding to a three-position four-way directional valve, and is equipped with a pressure transmitter to measure the hydraulic oil pressure.

[0038] The main oil tank 1 is connected to the P port of the external control valve group via a three-way ball valve 2 66, an external control pump group, and a one-way valve 4 68. The P port is connected to the A1 and B1 ports of the external control valve group via a high-pressure plate filter 2 72 and a three-position four-way directional valve 1 76-1, and is connected to the pilot control port 1. A pilot-operated proportional relief valve 69 is installed on the oil line between the P port and the high-pressure plate filter 2 72, and is connected to the T port of the external control valve group. This section of the oil line is also connected to a hydraulic bladder accumulator 70 located outside the external control valve group to eliminate pressure fluctuations, and a pressure transmitter 10 71-1 is installed to detect the oil pressure. The P port of the external control valve group is connected to the A2 and B2 ports of the external control valve group via a proportional pressure reducing valve 1 73 and a three-position four-way directional valve 2 76-2, and is connected to the pilot control port 2. A pressure transmitter 11 71-2 is installed on the oil line between the proportional pressure reducing valve 1 73 and the three-position four-way directional valve 2 76-2 to detect the oil pressure. The P port of the external control valve group sequentially passes through proportional pressure reducing valve 2 (74) and three-position four-way directional valve 3 (76-3), then outputs through ports A3 and B3 of the external control valve group, and is connected to pilot control port 3. A pressure transmitter 8 (46-4) is installed in the oil line between proportional pressure reducing valve 2 (74) and three-position four-way directional valve 3 (76-3) to detect oil pressure. The P port of the external control valve group sequentially passes through proportional pressure reducing valve 3 (75) and three-position four-way directional valve 4 (76-4), then outputs through ports A4 and B4 of the external control valve group, and is connected to pilot control port 4. A pressure transmitter 9 (46-5) is installed in the oil line between proportional pressure reducing valve 3 (75) and three-position four-way directional valve 4 (76-4) to detect oil pressure.

[0039] By organically combining all the above components, the hydraulic component's oil suction function (atmospheric pressure, booster pressure, negative pressure), leakage, load sensitivity, and pressure and flow tests during forward and reverse rotation of open and closed hydraulic components can be completed. Simultaneously, it can achieve oil replenishment, oil collection, hydraulic oil temperature control, and pilot control functions. The specific implementation of each function of the test bench is as follows: 1. For example Figure 2 As shown, the test of the oil suction function of hydraulic components is divided into the test of normal pressure oil suction function, the test of boosted pressure oil suction function, and the test of negative pressure oil suction function.

[0040] (1.1) During the test of the atmospheric pressure oil suction function, ball valve 3 16-3 is closed, and the hydraulic components draw oil directly from the main oil tank 1 through the thin ball valve 2 8-2 and ball valve 2 16-2. The main oil tank 1 is connected to the atmosphere through the moisture-absorbing air filter 4. At the same time, the pressure during atmospheric pressure oil suction is measured by pressure gauge 2 14-2 and pressure transmitter 2 15-2, thereby completing the test of the atmospheric pressure oil suction function.

[0041] (1.2) During the test of the boosting and suction function, ball valve 16-3 is closed. The hydraulic oil in the main oil tank 1 enters the inlet of the boosting pump group consisting of screw pump 9 and variable frequency motor 10 through thin ball valve 8-1. Variable frequency motor 10 drives screw pump 9 to boost the hydraulic oil to the required pressure. The hydraulic oil exceeding the required pressure overflows back into the main oil tank 1 through the boosting valve group consisting of pressure two-way cartridge valve 11, two-way cartridge valve cover plate 12 and proportional relief valve 13-1. The boosted hydraulic oil enters the hydraulic components through ball valve 16-1. At the same time, the pressure during boosting and suction is measured by pressure gauge 14-1 and pressure transmitter 15-1, thus completing the test of the boosting and suction function.

[0042] (1.3) When testing the negative pressure oil suction function, ball valve 3 16-3 is opened, and the hydraulic oil in the main oil tank 1 enters ball valve 2 16-2 through thin ball valve 1 8-1. By adjusting the opening of ball valve 2 16-2, negative pressure can be generated. The pressure during negative pressure oil suction is measured by pressure gauge 2 14-2 and pressure transmitter 2 15-2, thereby completing the test of the negative pressure oil suction function.

[0043] 2. For example Figure 2 As shown, during the hydraulic component leakage (internal leakage) test, when the leakage rate of the hydraulic component is less than or equal to the critical flow rate (16 L / min in this embodiment), the leaking hydraulic oil passes through the pipeline filter 19-1 and reaches the gear flow meter 21. At this time, the gear flow meter 21 can measure the leakage of the hydraulic component, and then returns to the main oil tank 1 through the check valve 23. Simultaneously, the pressure at the time of leakage is measured by the pressure gauge 14-3 and the pressure transmitter 18-1, thus completing the hydraulic component leakage test. When the leakage rate of the hydraulic component is greater than 16 L / min, the leaking hydraulic oil passes through the pipeline filter 20 and reaches the screw flow meter 22. At this time, the screw flow meter 22 can measure the leakage of the hydraulic component, and then returns to the main oil tank 1 through the check valve 17. Simultaneously, the pressure at the time of leakage is measured by the pressure gauge 14-4 and the pressure transmitter 18-2, thus completing the hydraulic component leakage test.

[0044] 3. For example Figure 3As shown, during the pressure and flow test of the load-sensitive hydraulic component, the oil inlet of the load-sensitive hydraulic component normally draws oil from the oil inlet circuit (corresponding to the oil inlet return assembly). The hydraulic oil from the outlet of the load-sensitive hydraulic component passes through the load-sensitive P-port valve group (i.e., two-way cartridge proportional throttle valve 28-1, two-way directional cartridge valve 24-2, two-way cartridge valve cover 29-1), high-pressure filter 30-1, and screw flow meter 31-1 to reach the control directional valve group. At this time, the two-position three-way shut-off directional valves 39-3 and 39-4 in the control directional valve group are energized, and the hydraulic oil flows through the directional valves... The two-way cartridge valve 624-6 and the two-way cartridge valve cover plate 829-5 lead to the loading valve assembly. The hydraulic oil exceeding the set pressure is controlled by the proportional relief valve 33 and the direct-acting relief valve 34 (the direct-acting relief valve 34 is used for safety). Hydraulic oil exceeding the set pressure returns to the main oil tank 1 through the two-way cartridge valve cover plate 225-1, the pressure two-way cartridge valve 235, the brazed plate radiator 40, and the three-way ball valve 42. Simultaneously, the hydraulic oil at the outlet passes through the solenoid ball valve 26 to the load-sensitive hydraulic oil port Ls of the hydraulic component. The load-sensitive working condition can be simulated by controlling the two-way cartridge proportional throttle valve 28-1. Pressure can be measured by the pressure gauge 514-5, the high-frequency pressure sensor 27-1, the pressure transmitter 1280-1, and the pressure transmitter 1380-2, and the flow rate can be measured by the screw flow meter 231-1.

[0045] 4. For example Figure 3 As shown, the pressure and flow rate test of the open hydraulic component during forward rotation is specifically implemented as follows: The high-speed motor 36 drives the open hydraulic component to rotate forward through the diaphragm coupling 37. At this time, the speed and torque can be measured by the torque tachometer 38. The oil inlet of the open hydraulic component normally draws oil from the oil inlet circuit. The hydraulic oil from the oil outlet of the open hydraulic component passes through the high-pressure filter 30-1 and the screw flow meter 31-1 to reach the control directional valve group. At this time, the two-position three-way shut-off directional valve 39-3 and the two-position three-way shut-off directional valve 49-4 are energized, and the hydraulic oil passes through the two-way cartridge valve 24-6 and the two-way cartridge valve cover plate 29-5 to the loading valve group.

[0046] At this time, the solenoid ball valve 32-2 is energized, and the hydraulic oil flows through the directional two-way cartridge valve 24-1 and the two-way cartridge valve cover plate 35-2 to the two-way cartridge proportional throttle valve 28-2. By controlling the two-way cartridge proportional throttle valve 28-2 to simulate a load, the hydraulic oil returns to the main oil tank 1 through the brazed plate radiator 40 and the three-way ball valve 42. Alternatively, the solenoid ball valve 32-2 can be de-energized, and by controlling the set pressure of the proportional relief valve 33, a load can be simulated. The hydraulic oil exceeding the set pressure of the proportional relief valve 33 and the direct-acting relief valve 34 returns to the main oil tank 1 through the two-way cartridge valve cover plate 25-1, the pressure two-way cartridge valve 35, the brazed plate radiator 40, and the three-way ball valve 42.

[0047] Pressure can be measured using pressure gauge 514-5, high-frequency pressure sensor 127-1, pressure transmitter 646-2, and pressure transmitter 746-3, while flow rate can be measured using screw flow meter 231-1.

[0048] 5. For example Figure 3 As shown, the pressure and flow rate test of the open hydraulic component during reverse rotation is specifically implemented as follows: The high-speed motor 36 drives the open hydraulic component to rotate in reverse through the diaphragm coupling 37. At this time, the speed and torque can be measured by the torque tachometer 38. The oil inlet of the open hydraulic component normally draws oil from the oil inlet circuit. The hydraulic oil from the oil outlet of the open hydraulic component passes through the high-pressure filter 30-2 and the screw flow meter 31-2 to reach the control directional valve group. At this time, the two-position three-way shut-off directional valve 39-3 and the two-position three-way shut-off directional valve 49-4 are energized, and the hydraulic oil passes through the two-way cartridge valve 5 24-5 and the two-way cartridge valve cover plate 7 29-4 to the loading valve group.

[0049] At this time, the solenoid ball valve 32-2 is energized, and the hydraulic oil flows through the directional two-way cartridge valve 24-1 and the two-way cartridge valve cover plate 35-2 to the two-way cartridge proportional throttle valve 28-2. By controlling the two-way cartridge proportional throttle valve 28-2 to simulate a load, the hydraulic oil returns to the main oil tank 1 through the brazed plate radiator 40 and the three-way ball valve 42. Alternatively, the solenoid ball valve 32-2 can be de-energized, and by controlling the set pressure of the proportional relief valve 33, a load can be simulated. The hydraulic oil exceeding the set pressure of the proportional relief valve 33 and the direct-acting relief valve 34 returns to the main oil tank 1 through the two-way cartridge valve cover plate 25-1, the pressure two-way cartridge valve 35, the brazed plate radiator 40, and the three-way ball valve 42.

[0050] Pressure can be measured using pressure gauge 614-6, high-frequency pressure sensor 27-2, pressure transmitter 646-2, and pressure transmitter 746-3, while flow rate can be measured using screw flow meter 31-2.

[0051] 6. For example Figure 3 As shown, the pressure and flow rate test of the closed hydraulic component during forward rotation is specifically implemented as follows: The high-speed motor 36 drives the closed hydraulic component to rotate forward through the diaphragm coupling 37. At this time, the speed and torque can be measured by the torque tachometer 38. The hydraulic oil from the outlet of the closed hydraulic component passes through the high-pressure filter 30-1 and the screw flow meter 31-1 to reach the control directional valve group. At this time, the two-position three-way shut-off directional valves 39-3 and 39-4 are energized, and the hydraulic oil passes through the two-way cartridge valve 24-6 and the two-way cartridge valve cover plate 29-5 to the loading valve group.

[0052] At this time, the solenoid ball valve 32-2 is energized, and the hydraulic oil passes through the directional two-way cartridge valve 24-1 and the two-way cartridge valve cover plate 35-2 to the two-way cartridge proportional throttle valve 28-2. By controlling the two-way cartridge proportional throttle valve 28-2 to simulate a load, the oil passes through the brazed plate radiator 40 and the three-way ball valve 42 to the replenishing valve assembly. Alternatively, the solenoid ball valve 32-2 can be de-energized, and by controlling the set pressure of the proportional relief valve 33 to simulate a load, the hydraulic oil exceeding the set pressure of the proportional relief valve 33 and the direct-acting relief valve 34 passes through the two-way cartridge valve cover plate 25-1, the pressure two-way cartridge valve 35, the brazed plate radiator 40, and the three-way ball valve 42 to the replenishing valve assembly.

[0053] After the hydraulic oil enters the replenishing valve assembly, the solenoid ball valve 39-2 is energized. The hydraulic oil then flows back to the closed hydraulic components through the two-way cartridge valve 7 24-7, the two-way cartridge valve cover plate 9 29-6, the two-way cartridge valve 4 24-4, the two-way cartridge valve cover plate 6 29-3, the screw flow meter 3 31-2, and the high-pressure filter 2 30-2 (the replenishing hydraulic oil actually only flows through the two-way cartridge valve 4 24-4). In addition, the required hydraulic oil is replenished to the closed hydraulic components through the replenishing circuit.

[0054] Pressure can be measured using pressure gauge 5 (14-5), pressure gauge 6 (14-6), high-frequency pressure sensor 1 (27-1), high-frequency pressure sensor 2 (27-2), pressure transmitter 6 (46-2), and pressure transmitter 7 (46-3), while flow rate can be measured using screw flow meter 2 (31-1) and screw flow meter 3 (31-2).

[0055] 7. For example Figure 3 As shown, the pressure and flow rate test of the closed hydraulic component during reverse rotation is specifically implemented as follows: The high-speed motor 36 drives the closed hydraulic component to rotate in reverse through the diaphragm coupling 37. At this time, the speed and torque can be measured by the torque tachometer 38. The hydraulic oil from the outlet of the closed hydraulic component passes through the high-pressure filter 30-2 and the screw flow meter 31-2 to reach the control directional valve group. At this time, the two-position three-way shut-off directional valves 39-3 and 39-4 are energized, and the hydraulic oil passes through the two-way cartridge valve 24-5 and the two-way cartridge valve cover 29-4 to the loading valve group.

[0056] At this time, the solenoid ball valve 32-2 is energized, and the hydraulic oil passes through the directional two-way cartridge valve 24-1 and the two-way cartridge valve cover plate 35-2 to the two-way cartridge proportional throttle valve 28-2. By controlling the two-way cartridge proportional throttle valve 28-2 to simulate the load, the oil passes through the brazed plate radiator 40 and the three-way ball valve 42 to the replenishing valve group. Alternatively, the solenoid ball valve 32-2 can be de-energized, and by controlling the set pressure of the proportional relief valve 33 to simulate the load, the hydraulic oil exceeding the set pressure of the proportional relief valve 33 and the direct-acting relief valve 34 passes through the two-way cartridge valve cover plate 25-1, the pressure two-way cartridge valve 35, the brazed plate radiator 40, and the three-way ball valve 42 to the replenishing valve group.

[0057] After the hydraulic oil enters the replenishing valve assembly, the solenoid ball valve 39-1 is energized. The hydraulic oil then returns to the closed hydraulic components through the two-way cartridge valve 24-7, the two-way cartridge valve cover plate 29-6, the two-way cartridge valve 24-3, the two-way cartridge valve cover plate 29-2, the screw flow meter 31-1, and the high-pressure filter 30-1. In addition, the replenishing circuit will replenish the closed hydraulic components with the required hydraulic oil.

[0058] Pressure can be measured using pressure gauge 5 (14-5), pressure gauge 6 (14-6), high-frequency pressure sensor 1 (27-1), high-frequency pressure sensor 2 (27-2), pressure transmitter 6 (46-2), and pressure transmitter 7 (46-3), while flow rate can be measured using screw flow meter 2 (31-1) and screw flow meter 3 (31-2).

[0059] 8. For example Figure 3 As shown, the hydraulic component's oil replenishment function is implemented as follows: the variable frequency motor 44 drives the hydraulic pump 43, which draws oil from the main oil tank 1 through the thin ball valve 65-2. The hydraulic oil passes through the high-pressure plate filter 45 and the high-pressure ball valve 47 to the oil replenishment port of the closed hydraulic component. Alternatively, it can return to the closed hydraulic component through the two-position three-way shut-off directional valve 39-5, the two-way directional cartridge valve 24-8, and the two-way cartridge valve cover plate 29-7. At this time, the oil replenishment pressure is controlled by the proportional relief valve 13-2 and the valve group composed of the pressure two-way cartridge valve 78 and the two-way cartridge valve cover plate 79. The oil replenishment pressure is measured by the pressure transmitter 46-1.

[0060] 9. For example Figure 4As shown, the oil collection function is implemented as follows during the test: the hydraulic oil leaked during the test of the hydraulic components will first be collected in the recovery oil tank 81. The recovery oil tank 81 is equipped with an air filter 49 that is connected to the atmosphere, and is also equipped with a float level switch 48 and a level and temperature gauge 50 to monitor the status of the recovery oil tank 81. The hydraulic oil in the recovery oil tank 81 will first pass through the suction filter 51 to the suction port of the oil recovery pump group composed of vane pump 52 and three-phase asynchronous motor 53, and then pass through pipeline filter 19-2 and pipeline filter 56 back to the main oil tank 1. The direct-acting relief valve 55 ensures that the pressure during recovery does not exceed the set value, and the pressure gauge 54-1 is used to display the pressure value during recovery.

[0061] 10. For example Figure 4 As shown, the hydraulic oil temperature control function is implemented as follows: When the hydraulic oil temperature is too high and needs to be cooled, the hydraulic oil in the main oil tank 1 passes through the thin ball valve 65-1 to the suction port of the circulating pump group composed of screw pump 63 and three-phase asynchronous motor 64-1, and then returns to the main oil tank 1 through pipeline filter 61, pipeline filter 60, brazed plate radiator 58 and check valve 57. During this process, the solenoid water valve 59 is energized to open the cooling water, and the direct-acting overflow valve 62 ensures that the pressure during circulation does not exceed the set value. The pressure gauge 54-2 is used to display the pressure value during circulation, thereby realizing the function of hydraulic oil cooling. When the temperature drops to the set temperature value of the liquid level thermometer 7, the solenoid water valve 59 is de-energized to close the cooling water, and the circulating pump group stops working at the same time.

[0062] When the hydraulic oil temperature is too low and heating is required, the hydraulic oil in the main oil tank 1 passes through the thin ball valve 65-1 to the suction port of the circulating pump group consisting of the screw pump 63 and the three-phase asynchronous motor 64-1. Then, it passes through the pipeline filter 61, the pipeline filter 60, the brazed plate radiator 58, and the check valve 57 back to the main oil tank 1. At the same time, the solenoid water valve 59 is de-energized and shuts off the cooling water. The sheathed tubular heater 5 starts heating. The direct-acting relief valve 62 ensures that the pressure during circulation does not exceed the set value. The pressure gauge 54-2 is used to display the pressure value during circulation, thereby realizing the function of hydraulic oil heating. When the temperature reaches the set value of the liquid level thermometer 7, the sheathed tubular heater 5 stops heating, and the circulating pump group stops working at the same time.

[0063] 11. For example Figure 5As shown, the hydraulic oil pilot control function is implemented (different pilot control ports are selected according to the actual required range). When pilot control port 1 (applicable range is 0-13MPa) is used for control, the three-phase asynchronous motor 64-2 drives the vane pump 67, which draws oil from the main oil tank 1 through the three-way ball valve 66. The hydraulic oil passes through the check valve 68 and the high-pressure plate filter 72 to the three-position four-way directional valve 76-1. If the three-position four-way directional valve 76-1 is energized, the hydraulic oil flows from pilot control port 1 to the hydraulic components. The hydraulic oil pressure is controlled by adjusting the pilot-operated proportional relief valve 69. If the three-position four-way directional valve 76-1 is de-energized, the hydraulic oil returns from the hydraulic components to the main oil tank 1. At the same time, pressure fluctuations can be eliminated by the hydraulic bladder accumulator 70, and the pressure transmitter 71-1 measures the pilot control pressure.

[0064] When pilot control port 2 (applicable range 0-10MPa) is used for control, the three-phase asynchronous motor 64-2 drives vane pump 67, which draws oil from the main oil tank 1 through the three-way ball valve 66. The hydraulic oil passes through check valve 68, high-pressure plate filter 72, and proportional pressure reducing valve 73 to the three-position four-way directional valve 76-2. If the three-position four-way directional valve 76-2 is energized, the hydraulic oil flows from pilot control port 2 to the hydraulic components. The hydraulic oil pressure is controlled by adjusting the proportional pressure reducing valve 73. If the three-position four-way directional valve 76-2 is de-energized, the hydraulic oil returns from the hydraulic components to the main oil tank 1. Simultaneously, pressure fluctuations can be eliminated through the hydraulic bladder accumulator 70, and the pressure transmitter 71-2 measures the pilot control pressure.

[0065] When pilot control port 3 (applicable range 0-8MPa) is used for control, the three-phase asynchronous motor 364-2 drives vane pump 267, which draws oil from the main oil tank 1 through the three-way ball valve 266. The hydraulic oil passes through check valve 468, high-pressure plate filter 272, and proportional pressure reducing valve 274 to the three-position four-way directional valve 376-3. If the three-position four-way directional valve 376-3 is energized, the hydraulic oil flows from pilot control port 3 to the hydraulic components. The hydraulic oil pressure is controlled by adjusting the proportional pressure reducing valve 274. If the three-position four-way directional valve 376-3 is de-energized, the hydraulic oil returns from the hydraulic components to the main oil tank 1. Simultaneously, pressure fluctuations can be eliminated through the hydraulic bladder accumulator 70, and the pressure transmitter 846-4 measures the pilot control pressure.

[0066] When pilot control port 4 (applicable range 0-5MPa) is used for control, the three-phase asynchronous motor 364-2 drives vane pump 267, drawing oil from the main oil tank 1 through three-way ball valve 266. The hydraulic oil passes through check valve 468, high-pressure plate filter 272, and proportional pressure reducing valve 375 to the three-position four-way directional valve 476-4. If the three-position four-way directional valve 476-4 is energized, the hydraulic oil flows from pilot control port 4 to the hydraulic components. The hydraulic oil pressure is controlled by adjusting the proportional pressure reducing valve 375. If the three-position four-way directional valve 476-4 is de-energized, the hydraulic oil returns from the hydraulic components to the main oil tank 1. Simultaneously, pressure fluctuations can be eliminated through hydraulic bladder accumulator 70, and pressure transmitter 946-5 measures the pilot control pressure.

[0067] This invention is mainly used in the hydraulic industry of engineering machinery. It is an integrated testing platform that combines multiple types, multiple working conditions, and multiple parameters. It can play an important role in product development, maintenance and other activities, and can well meet the needs of the industry.

[0068] It will be understood by those skilled in the art that the above descriptions are merely preferred examples of the invention and are not intended to limit the invention. Although the invention has been described in detail with reference to the foregoing examples, those skilled in the art can still modify the technical solutions described in the foregoing examples or make equivalent substitutions for some of the technical features. All modifications and equivalent substitutions made within the spirit and principles of the invention should be included within the scope of protection of the invention.

Claims

1. A test bench for high-speed hydraulic pumps and multi-way valves used in engineering machinery, characterized in that, include: Main oil tank, oil suction and return assembly, hydraulic component performance testing assembly, oil collection assembly, hydraulic oil temperature control assembly, pilot control assembly; The oil suction and return assembly includes a normal pressure oil suction circuit, a booster oil suction circuit, and a negative pressure oil suction circuit, which are respectively connected to the two oil suction ports of the hydraulic element and the main oil tank. The oil circuit switching is controlled by the valve body. It also includes two return oil circuits with different ranges, which are respectively connected to the two oil return ports of the hydraulic element and the main oil tank. The hydraulic component performance testing assembly uses a load-sensitive P-port valve group, an Ls-port valve group, a control directional valve group, and a loading valve group to test the pressure and flow of load-sensitive hydraulic components. It also uses the control directional valve group and the loading valve group to test the pressure and flow of open hydraulic components during forward or reverse rotation, and uses the control directional valve group, the loading valve group, and the replenishing valve group to test the pressure and flow of closed hydraulic components during forward or reverse rotation. The P1 port of the control directional valve group is connected to the P port of the loading valve group. The T port of the loading valve group is connected to a three-way ball valve through a brazed plate radiator. One output of the three-way ball valve is connected to the main oil tank, and the other output is connected to the T1 port of the replenishing valve group. The replenishing valve group works in conjunction with the control directional valve group to return hydraulic oil to the hydraulic components. In the oil collection assembly, the leaked hydraulic oil from the hydraulic components flows into the main oil tank in sequence through the recovery oil tank, the suction filter, the leakage recovery pump set, and the pipeline filter. In the hydraulic oil temperature control component, the hydraulic oil in the main oil tank flows back to the main oil tank after passing through the valve body, circulating pump group, pipeline filter, brazed plate radiator, and check valve in sequence; the brazed plate radiator is connected to the cooling water through the valve body to achieve hydraulic oil cooling, and the sheathed tubular oil heater installed on the main oil tank is used to achieve hydraulic oil heating. In the pilot control assembly, the hydraulic oil in the main oil tank passes sequentially through a ball valve, an external control pump group, a check valve, and a high-pressure plate filter, and then is diverted to multiple sets of proportional pressure reducing valves and three-position four-way directional valves with different parameters, and flows into the corresponding pilot control port under control.

2. The test bench for high-speed hydraulic pumps and multi-way valves for engineering machinery according to claim 1, characterized in that, The control directional valve assembly comprises four units. The first unit includes a 2-way cartridge valve (3), a 2-way cartridge valve cover plate (5), and a 2-position 3-way shut-off directional valve (1). The second unit includes a 2-way cartridge valve (4), a 2-way cartridge valve cover plate (6), and a 2-position 3-way shut-off directional valve (2). The third unit includes a 2-way cartridge valve (5), a 2-way cartridge valve cover plate (7), and a 2-position 3-way shut-off directional valve (3). The fourth unit includes a 2-way cartridge valve (6), a 2-way cartridge valve cover plate (8), and a 2-position 3-way shut-off directional valve (4). In the de-energized state, ports B and C of the four two-position three-way shut-off directional valves are open; in the energized state, ports A and C are open. Ports A and B of each unit's two-position three-way shut-off directional valve are connected to the main oil circuit of the two-way cartridge valve, and port C is connected to the cover plate of the two-way cartridge valve. Port B of two-position three-way shut-off directional valve one and two-position three-way shut-off directional valve four is connected to port A of the control directional valve group; port B of two-position three-way shut-off directional valve two and two-position three-way shut-off directional valve three is connected to port B of the control directional valve group; port A of two-position three-way shut-off directional valve one and two-position three-way shut-off directional valve two is connected to port P of the control directional valve group; port A of two-position three-way shut-off directional valve three and two-position three-way shut-off directional valve four is connected to port P1 of the control directional valve group.

3. The test bench for high-speed hydraulic pumps and multi-way valves for engineering machinery according to claim 1, characterized in that, The loading valve assembly includes two oil circuits from port P to port T. The first oil circuit is equipped with a valve assembly consisting of a directional two-way cartridge valve, a two-way cartridge valve cover plate, and a solenoid ball valve, as well as a two-way cartridge proportional throttle valve. The second oil circuit is equipped with a valve assembly consisting of a solenoid ball valve, a proportional relief valve, a direct-acting relief valve, a pressure two-way cartridge valve, and a two-way cartridge valve cover plate. When the solenoid ball valve is energized, pressurized oil flows into the first oil circuit and simulates a load by controlling the two-way cartridge proportional throttle valve. When de-energized, pressurized oil flows into the second oil circuit and simulates a load by controlling the set pressure of the proportional relief valve.

4. The test bench for high-speed hydraulic pumps and multi-way valves for engineering machinery according to claim 1, characterized in that, In the hydraulic component performance testing assembly, the hydraulic component rotates under the control of a high-speed motor. Port A of the hydraulic component is connected to three oil circuits. One circuit is connected to the load-sensitive port P through a load-sensitive port P valve group, which includes a directional two-way cartridge valve, a two-way cartridge proportional throttle valve, and a two-way cartridge valve cover. The second circuit is connected to the Ls port through an Ls port valve group, which includes a solenoid ball valve. The third circuit is connected to the A port of the control directional valve group through a high-pressure filter and a screw flow meter. Port B of the hydraulic component is connected to the B port of the control directional valve group through a high-pressure filter and a screw flow meter.

5. The test bench for high-speed hydraulic pumps and multi-way valves for engineering machinery according to claim 1, characterized in that, The oil circuit connecting the T1 port and P1 port of the replenishing valve assembly is equipped with a directional two-way cartridge valve and a two-way cartridge valve cover plate. The P port of the replenishing valve assembly is connected to the main oil tank through a replenishing pump assembly consisting of a hydraulic pump and a variable frequency motor, and a thin ball valve. After passing through a high-pressure plate filter, the P port of the replenishing valve assembly outputs oil to the replenishing port of the hydraulic component from the S port. The oil circuit between the high-pressure plate filter and the S port of the replenishing valve assembly is connected to the P1 port of the replenishing valve assembly through a valve assembly consisting of a directional two-way cartridge valve, a two-way cartridge valve cover plate, and a two-position three-way shut-off directional valve. The oil circuit between the high-pressure plate filter and the S port of the replenishing valve assembly is connected to the T port of the replenishing valve assembly through a valve assembly consisting of a pressure two-way cartridge valve, a two-way cartridge valve cover plate, and a proportional relief valve.

6. The test bench for high-speed hydraulic pumps and multi-way valves for engineering machinery according to claim 1, characterized in that, In the oil suction and return assembly, the oil suction port 1 of the hydraulic component is connected to the main oil tank in sequence through ball valve 1, booster pump group, and thin ball valve 1; the oil suction port 2 is connected to the main oil tank in sequence through ball valve 2 and thin ball valve 2; the oil passage between ball valve 1 and booster pump group is connected to the oil passage between ball valve 2 and thin ball valve 2 through ball valve 3; the oil passage between ball valve 1 and booster pump group is also connected to the main oil tank through booster valve group; the booster valve group includes pressure two-way cartridge valve 1, two-way cartridge valve cover plate 1, and proportional relief valve 1; In the oil suction and return assembly, the return port 1 of the hydraulic component is connected to the main oil tank in sequence through pipeline filter one, gear flow meter, and check valve two, and the return port 2 is connected to the main oil tank in sequence through pipeline filter three, screw flow meter one, and check valve one.

7. The test bench for high-speed hydraulic pumps and multi-way valves for engineering machinery according to claim 1, characterized in that, The pilot control assembly includes four pilot control ports, each corresponding to a three-position four-way directional valve, and is equipped with a pressure transmitter to measure the hydraulic oil pressure. The main oil tank is connected to the P port of the external control valve group via a three-way ball valve, an external control pump group, a check valve, and the external control valve group in sequence. The P port is connected to the A1 and B1 ports of the external control valve group via a high-pressure plate filter and a three-position four-way directional valve one, and is connected to the pilot control port 1. The oil circuit between the P port of the external control valve group and the high-pressure plate filter is connected to a hydraulic bladder accumulator arranged outside the external control valve group. The P port of the external control valve group is connected to the A2 and B2 ports of the external control valve group in sequence via a proportional pressure reducing valve one and a three-position four-way directional valve two, and is connected to the pilot control port 2. The P port of the external control valve group is connected to the A3 and B3 ports of the external control valve group in sequence via a proportional pressure reducing valve two and a three-position four-way directional valve three, and is connected to the pilot control port 3. The P port of the external control valve group is connected to the A4 and B4 ports of the external control valve group in sequence via a proportional pressure reducing valve three and a three-position four-way directional valve four, and is connected to the pilot control port 4.

8. The test bench for high-speed hydraulic pumps and multi-way valves for engineering machinery according to claim 2, characterized in that, During the pressure and flow test of the load-sensitive hydraulic component, the oil inlet of the load-sensitive hydraulic component draws oil through the oil inlet and outlet assembly. The hydraulic oil from the outlet of the load-sensitive hydraulic component passes through the load-sensitive P-port valve group, high-pressure filter one, and screw flow meter two to reach the control directional valve group. At this time, the two-position three-way shut-off directional valve three and two-position three-way shut-off directional valve four in the control directional valve group are energized, and the hydraulic oil enters the loading valve group through the two-way cartridge valve six and the two-way cartridge valve cover plate eight. The hydraulic oil exceeding the set pressure of the relief valve is output from the T port of the loading valve group and flows back to the main oil tank. At the same time, the hydraulic oil from the outlet reaches the Ls port of the hydraulic component through the solenoid ball valve. Pressure is measured at various points using pressure gauges, high-frequency pressure sensors, and pressure transmitters, while flow rate is measured using screw flow meters.

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