Testing device and testing method for testing performance of hydraulic hoist

Abstract

The invention relates to the technical field of hydraulic hoists, in particular to a testing device and a testing method for testing the performance of a hydraulic hoist, the testing device comprises a testing oil cylinder, a loading oil cylinder, a hydraulic system and an electric control cabinet, and the testing oil cylinder and the loading oil cylinder are connected into a whole. The tension and pressure between the test oil cylinder and the loading oil cylinder become the system internal force of the whole structure, external force intervention is reduced, the test accuracy is improved, meanwhile, the load equivalence principle is adopted, the door opening time and the door closing time of the rapid hydraulic hoist are set, the load capacity of the rapid hydraulic hoist under different test working conditions can be simulated, and the test efficiency is improved. Therefore, various performances of the rapid hydraulic hoist can be observed, and the test device satisfying the performance test of the rapid hydraulic hoist is provided. According to the test method, the pump station and the control valve group are controlled to act through the electrical control cabinet, the labor intensity of workers is reduced, the test cost is saved, the test convenience can be improved, and the test accuracy is improved through the test device.

Description

Technical Field

[0001] The invention relates to the technical field of hydraulic gate hoists, and in particular to a test device and a test method for testing the performance of a hydraulic gate hoist. Background Art

[0002] Hydraulic gate hoists are often used in water conservancy and hydropower projects. They are generally composed of a hydraulic system and a hydraulic cylinder. Under the control of the hydraulic system, the piston in the hydraulic cylinder makes axial reciprocating motion along the inner wall, thereby driving the piston rod and the valve connected to the piston rod to make linear reciprocating motion, thereby achieving the purpose of opening and closing the valve. The reliability requirements of hydraulic gate hoists are very high. For valves with strict opening and closing time requirements, if the hydraulic gate hoist cannot be opened or closed within the specified time, it will cause losses to varying degrees, and may even affect the passage time of ships and cause system chaos.

[0003] Because the dynamic water state is difficult to simulate, the existing hydraulic gate hoists are usually tested for various performance tests before leaving the factory by a no-load test. The valve is opened or closed by the hydraulic gate hoist without water pressure, and the opening and closing force, opening and closing speed and opening and closing time of the hydraulic gate hoist are measured to detect the various performances of the hydraulic gate hoist. However, it is actually impossible to determine the load capacity of the fast hydraulic gate hoist only by performing a no-load test on the hydraulic gate hoist, nor is it possible to judge the various performances of the hydraulic gate hoist in rapid opening and closing conditions under different loads and different working conditions, resulting in low accuracy of the performance test of the existing hydraulic gate hoist.

[0004] A multi-stage water-saving ship lock is used in a water conservancy hub. The filling and discharge steps are significantly increased compared with ordinary ship locks. The hub has a huge volume of ships passing through it. It is necessary to achieve the goal of water saving while ensuring the passage efficiency of ships. The opening and closing speed of the hydraulic gate hoist of the ship lock needs to reach 8-16m / min, which is several times the opening and closing speed of 2-4m / min of the conventional hydraulic gate hoist, and it needs to be able to force the door to close in an emergency. Therefore, how to provide accurate data support for the fast opening and closing hydraulic gate hoist through performance testing has become a technical problem that needs to be solved urgently. Summary of the invention

[0005] The purpose of the present invention is to overcome the shortcomings of the prior art that the performance test of the existing hydraulic gate hoist has low accuracy and cannot provide accurate data support for the rapid hydraulic gate hoist, and to provide a test device and test method for the performance test of the hydraulic gate hoist.

[0006] In a first aspect, the present invention provides a test device for testing the performance of a hydraulic hoist, comprising a test cylinder, a loading cylinder, a hydraulic system and an electrical control cabinet; The test cylinder and the loading cylinder are supported by a bracket, coaxially and horizontally arranged, the lower end cover of the test cylinder and the upper end cover of the loading cylinder are rigidly connected by a sleeve, and the piston rod of the test cylinder and the piston rod of the loading cylinder are rigidly connected in the sleeve; The hydraulic system includes a pump station and a control valve group. The pump station includes a variable piston pump group and a hydraulic oil tank. The hydraulic system is connected to the test cylinder and the loading cylinder respectively. The electrical control cabinet is used to control the action of the hydraulic system, adjust the interaction force between the test cylinder and the loading cylinder, and simulate the load capacity of the fast hydraulic hoist under the test conditions. The test conditions include any one of the door opening conditions, door closing conditions and accident door closing conditions. In the door opening condition, the pump station delivers oil to the rod chamber of the test cylinder, the loading cylinder provides a load-equivalent pulling force to the test cylinder, and the piston rod of the test cylinder retracts within the set door opening time; In the closed-door working condition, the pump station delivers oil to the rod chamber of the loading cylinder, and the loading cylinder provides a load-equivalent pulling force to the test cylinder, and the piston rod of the test cylinder extends within the set closed-door time; During the accidental closing condition, the pump station delivers oil to the rodless chamber of the test cylinder, and the loading cylinder provides a back pressure thrust equivalent to the load to the test cylinder, and the piston rod of the test cylinder extends within the set closing time.

[0007] The test device for the performance test of a hydraulic gate hoist of the present invention adopts the load equivalence principle, and can equate the gate gravity, water flow lifting force, water column force and friction resistance actually received by the rapid hydraulic gate hoist to the pulling force or thrust of the loading cylinder, and set the gate opening time and gate closing time that meet the requirements of the rapid hydraulic gate hoist, and can simulate the load capacity of the rapid hydraulic gate hoist under different test conditions, so as to observe various performances of the rapid hydraulic gate hoist, and provide a test device that meets the requirements of the performance test of the rapid hydraulic gate hoist; By setting the test cylinder and the loading cylinder horizontally, the requirements for the site can be reduced to meet the performance test of large-scale rapid hydraulic hoists; By rigidly connecting the test cylinder and the loading cylinder with a sleeve, and rigidly connecting the piston rod of the test cylinder and the piston rod of the loading cylinder in the sleeve, the test cylinder and the loading cylinder become a whole, and the tension and pressure between the test cylinder and the loading cylinder become the internal force of the system of the overall structure, which can reduce the intervention of external forces in the system and improve the accuracy of the test.

[0008] Preferably, during the door opening condition, the pump station delivers oil to the rod chamber of the test cylinder through the first cartridge overflow valve group, the test cylinder works under the set pressure of the first cartridge overflow valve group, and the rodless chamber of the test cylinder is connected with the hydraulic oil tank; the rod chamber of the loading cylinder is connected with the return oil of the hydraulic oil tank through the second cartridge overflow valve group, and the hydraulic oil tank is connected with the rodless chamber of the loading cylinder for oil replenishment, and adjusting the second cartridge overflow valve group can achieve load equivalence of the door opening condition.

[0009] The piston rod of the test cylinder is retracted to simulate the door opening condition, and the return oil pressure of the rod chamber of the loading cylinder is adjusted to continuously provide the test cylinder with a pulling force equivalent to the door opening condition. In this way, the gate gravity, water flow lifting force, water column force and frictional resistance in the door closing condition can be accurately simulated through accurate adjustment of the second plug-in relief valve group, providing an accurate equivalent load force for the test cylinder and improving the test accuracy.

[0010] Preferably, in closed-door working conditions, the pump station is connected to the rod chamber of the loading cylinder, the loading cylinder works under the set pressure of the second cartridge relief valve group, and the rodless chamber of the loading cylinder is connected to the return oil of the hydraulic tank; the rod chamber of the test cylinder is connected to the rodless chamber of the test cylinder through the first differential circuit, the first differential circuit includes a third cartridge relief valve group, the third cartridge relief valve group is connected to the first reversing valve, and the rodless chamber of the test cylinder is connected to the oil tank replenishing circuit; adjusting the third cartridge relief valve group can achieve load equivalence in closed-door working conditions.

[0011] The piston rod of the test cylinder is extended to simulate the closed-door working condition, and the pressure of the rod chamber of the loading cylinder reaches an appropriate load force through the second cartridge relief valve group. By adjusting the oil outlet pressure of the rod chamber of the test cylinder, the test cylinder is continuously provided with a pulling force equivalent to the closed-door working condition. In this way, the combination of the second cartridge relief valve group and the third cartridge relief valve group can accurately simulate the water flow lifting force, water column force and frictional resistance in the closed-door working condition, provide the test cylinder with an accurate closed-door load, and further improve the test accuracy. At the same time, the oil in the rod chamber of the test cylinder is returned to the rodless chamber of the test cylinder through the first differential circuit, and the rodless chamber of the test cylinder is further replenished with oil through the oil tank replenishing circuit, which can quickly increase the flow of the rodless chamber of the test cylinder and make the cylinder run faster to meet the rapid opening and closing requirements of the rapid hydraulic gate opening and closing machine.

[0012] Preferably, a first accumulator group is provided between the rod chamber of the test cylinder and the pump station, and in closed-door working condition, the pressure of the rod chamber of the test cylinder is stabilized by the first accumulator group.

[0013] Preferably, the first differential circuit also includes a cartridge proportional valve group, which is arranged between the third cartridge overflow valve group and the rodless chamber of the test cylinder, and the cartridge proportional valve group is connected to an auxiliary power source; in closed-door working conditions, adjusting the cartridge proportional valve group can achieve buffering control of the test cylinder.

[0014] Preferably, the oil tank replenishment circuit includes a high-position oil tank and a first cartridge valve, the high-position oil tank is arranged on the side of the rodless cavity close to the test cylinder, the high-temperature oil tank is arranged at a position higher than the test cylinder, and the high-position oil tank is connected to the hydraulic oil tank pipeline. This can realize the rapid replenishment of the rodless cavity of the test cylinder, so that the test cylinder meets the rapid opening and closing requirements of the rapid hydraulic hoist.

[0015] Preferably, the first cartridge overflow valve group is connected to the second reversing valve; in the accident closed-door working condition, the pump station is connected to the rodless chamber of the test cylinder, and the rod chamber of the test cylinder is connected to the rodless chamber of the test cylinder through the second differential circuit, and the test cylinder operates under the set pressure of the first cartridge overflow valve group; the rodless chamber of the loading cylinder is connected to the return oil of the hydraulic oil tank through the fourth cartridge overflow valve group, and the hydraulic oil tank is connected to the rod chamber of the loading cylinder for replenishing oil, and adjusting the fourth cartridge overflow valve group can achieve load equivalence in the accident closed-door working condition.

[0016] The piston rod of the test cylinder is extended under the combined action of the pump station input pressure and the back pressure of the loading cylinder, simulating the accidental door closing working condition. The rodless chamber pressure of the loading cylinder is adjusted through the fourth plug-in relief valve group to provide the test cylinder with an accurate accidental door closing back pressure load, further improving the test accuracy. The rod chamber oil of the test cylinder flows to the rodless chamber of the test cylinder through the second differential circuit, and the rodless chamber of the test cylinder is replenished with oil, making the cylinder run faster to meet the rapid opening and closing requirements of the rapid hydraulic gate opening and closing machine.

[0017] Preferably, a second accumulator group is provided between the rodless chamber of the loading cylinder and the hydraulic oil tank, and in an emergency door closing condition, the pressure of the rodless chamber of the loading cylinder is stabilized by the second accumulator group.

[0018] Preferably, the second differential circuit includes a one-way valve. In the closed-door emergency condition, the rod chamber of the test cylinder is connected to the rodless chamber of the test cylinder through the one-way valve, and the output flow of the pump station is adjusted to achieve buffer control of the test cylinder.

[0019] Preferably, the first cartridge relief valve group is connected to the second reversing valve, the third cartridge relief valve group is connected to the first reversing valve; the first cartridge reversing valve group is provided between the pump station and the rodless chamber of the test cylinder, the second cartridge reversing valve group is provided between the pump station and the rod chamber of the test cylinder, the third cartridge reversing valve group is provided between the pump station and the rod chamber of the loading cylinder, the fourth cartridge reversing valve group is provided between the pump station and the rodless chamber of the loading cylinder; the second cartridge valve is provided between the hydraulic oil tank and the rod chamber of the loading cylinder. This realizes the control of the hydraulic oil circuit between the pump station and the test oil cylinder and the loading oil cylinder.

[0020] Preferably, the second reversing valve includes a 1DT end electromagnet, the first cartridge reversing valve group includes a 2DT end electromagnet, the cartridge proportional valve group includes a 3DT end electromagnet, the first reversing valve includes a 4DT end electromagnet, the second cartridge reversing valve group includes a 5DT end electromagnet, the third cartridge reversing valve group includes a 6DT end electromagnet, and the fourth cartridge reversing valve group includes a 7DT end electromagnet; in the door opening condition, the 1DT end electromagnet, the 5DT end electromagnet and the 7DT end electromagnet are energized at the same time; in the door closing condition, the 1DT end electromagnet, the 3DT end electromagnet, the 4DT end electromagnet, the 6DT end electromagnet and the 7DT end electromagnet are energized at the same time; in the accident door closing condition, the 1DT end electromagnet, the 2DT end electromagnet and the 3DT end electromagnet are energized at the same time.

[0021] Preferably, the rod chamber of the test cylinder is connected to a first pressure sensor, the rodless chamber of the test cylinder is connected to a second pressure sensor, the rod chamber of the loading cylinder is connected to a third pressure sensor, the rodless chamber of the loading cylinder is connected to a fourth pressure sensor, and the oil outlet of the pump station is connected to a fifth pressure sensor, and all pressure sensors are respectively connected to the electrical control cabinet for communication. This enables real-time collection of pressure data of each chamber under test conditions, so that accurate pressure adjustment of the equivalent load can be performed through the electrical control cabinet to improve the accuracy of the test.

[0022] Preferably, the rodless cavity of the loading cylinder is connected to a first displacement sensor, and the rodless cavity of the test cylinder is connected to a second displacement sensor, and the first displacement sensor and the second displacement sensor are respectively connected to the electrical control cabinet for communication, so as to realize the real-time collection of the piston rod position data under the test condition, so as to adjust the pressure to match the opening and closing time of the fast hydraulic hoist through the electrical control cabinet, and further improve the accuracy of the test.

[0023] Preferably, the electrical control cabinet includes a manual control mode, which can select and set any test condition of the hydraulic gate hoist, perform simulation tests of any test condition, and collect and store data.

[0024] Preferably, the electrical control cabinet includes a remote control mode, which can select and set any test condition of the hydraulic gate hoist or the interval between two adjacent test conditions through the host computer, conduct a simulation test of any test condition or an automatic switching simulation test of multiple test conditions, and collect and store data. By remotely operating the host computer, not only can the test device work effectively and automatically, but it also has the ability to switch test conditions and collect and store data such as travel and pressure, which can greatly reduce manual labor intensity and save testing costs.

[0025] Preferably, the pump station includes several variable piston pump motor groups, and the number of variable piston pump motor groups started in any test condition is positively correlated with the opening and closing speed requirements of the corresponding test condition. The pump station can start an appropriate number of variable piston pumps according to the test condition requirements to meet the test condition requirements and reduce the overall energy consumption of the test device.

[0026] Preferably, the bracket includes a cover plate and a bottom support, which are detachably connected to form a clamping channel adapted to the shape of the test cylinder, the loading cylinder and the sleeve, and a bottom plate is provided at the bottom of the bottom support, and the bracket is a steel structure. The test cylinder and the loading cylinder are stably supported to avoid vibration of the test device under the test condition, and to ensure that the tension and pressure between the test cylinder and the loading cylinder are the internal forces of the test cylinder-sleeve-loading cylinder system, reducing the intervention of external forces in the system, thereby improving the accuracy of the test.

[0027] In a second aspect, the present invention provides a test method for testing the performance of a hydraulic gate hoist, comprising the following steps: S1. According to the test condition parameter requirements, a test device for testing the performance of a hydraulic gate hoist as described above is established; S2. Through the electrical control cabinet, simulate the door opening condition, door closing condition and accident door closing condition in manual control mode or remote control mode, and collect and store data.

[0028] A test method for testing the performance of a hydraulic gate hoist of the present invention controls the action of a pump station and a control valve group through an electrical control cabinet, can facilitate the effective operation of the test device under different test conditions, reduce manual labor intensity and save test costs, and can improve the convenience of the test. Through the above-mentioned test device, a fast hydraulic gate hoist can achieve a fast and accurate response within the set door opening and closing time, thereby improving the accuracy of the test.

[0029] Preferably, S2 comprises: S2.1. Carry out the door opening working condition test, supply oil to the rod chamber of the test cylinder through the pump station, and adjust the outlet pressure of the rod chamber of the loading cylinder through the second plug-in relief valve group, so that the loading cylinder provides a pulling force equivalent to the door opening load to the test cylinder; S2.2. Conduct a closed-door working condition test, deliver oil to the rod chamber of the loading cylinder through the pump station, adjust the outlet pressure of the rod chamber of the loading cylinder through the second plug-in relief valve group, so that the rod chamber of the loading cylinder reaches an equivalent load force, and replenish oil to the rodless chamber of the test cylinder under the set pressure through the oil tank oil replenishment circuit and the first differential circuit, so that the loading cylinder provides a pulling force equivalent to the closed-door load to the test cylinder; S2.3, cycle S2.1-S2.2 several times; S2.4, conduct the accident closed door working condition test, the pump station delivers oil to the rodless chamber of the test cylinder, and adjusts the rodless chamber outlet pressure of the loading cylinder through the fourth plug-in relief valve group, so that the loading cylinder provides the test cylinder with a back pressure thrust equivalent to the accident closed door load, so as to realize the effective and automatic operation of the test device.

[0030] Compared with the prior art, the present invention has the following beneficial effects: 1. The present invention provides a test device for testing the performance of a hydraulic gate hoist. By adopting the load equivalence principle, the gate gravity, water flow lifting force, water column force and friction resistance actually exerted on the rapid hydraulic gate hoist are equivalent to the pulling force or thrust of the loading cylinder, and the gate opening time and gate closing time that meet the requirements of the rapid hydraulic gate hoist are set. The load capacity of the rapid hydraulic gate hoist under different test conditions can be simulated, so as to observe various performances of the rapid hydraulic gate hoist, and provide a test device that meets the requirements of the performance test of the rapid hydraulic gate hoist; 2. The present invention provides a test device for testing the performance of a hydraulic gate hoist. By horizontally arranging the test cylinder and the loading cylinder, the requirements for the site can be reduced, and the performance test of a large-scale rapid hydraulic gate hoist can be met; 3. The present invention provides a test device for testing the performance of a hydraulic gate hoist, which rigidly connects a test cylinder and a loading cylinder with a sleeve, and rigidly connects the piston rod of the test cylinder and the piston rod of the loading cylinder in the sleeve, so that the test cylinder and the loading cylinder become a whole, and the tension and pressure between the test cylinder and the loading cylinder become the system internal force of the whole structure, which can reduce the intervention of external forces in the system and improve the accuracy of the test; 4. The present invention provides a test method for testing the performance of a hydraulic gate hoist. By controlling the action of the pump station and the control valve group through an electrical control cabinet, the test device can be facilitated to work effectively under different test conditions, reduce manual labor intensity and save test costs, and can improve the convenience of the test. Through the above-mentioned test device, the rapid hydraulic gate hoist can achieve rapid and accurate response within the set opening and closing door time, thereby improving the accuracy of the test. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 It is a structural schematic diagram of the test cylinder and the loading cylinder combination in Example 1; Figure 2 for Figure 1 The schematic diagram of the local enlarged structure at M in the middle; Figure 3 It is a structural schematic diagram of the pump station in Example 1; Figure 4 A schematic diagram of the structure of a test device for testing the performance of a hydraulic gate hoist according to Example 1; Figure 5 A schematic diagram of a hydraulic system of a test device for testing the performance of a hydraulic gate hoist in Example 1; Figure 6 The electrical operation diagram of the test device in Example 1 under different test conditions; Figure 7 This is a control loop diagram of the manual control mode in Example 1; Figure 8 This is the hardware configuration diagram of the electrical control cabinet; Fig. 9 It is the PLC configuration diagram of the electrical control cabinet; Fig.10 This is a test data diagram of a large ship lock in the door opening-closing condition in Example 2; Fig.11 This is a test data diagram of a large ship lock in Example 2 under the gate opening-accident closing working condition; Markings in the figure: 1-test cylinder, 11-rodless chamber of test cylinder, 12-rod chamber of test cylinder, 2-loading cylinder, 21-loading cylinder rod chamber, 22-loading cylinder rodless chamber, 3-sleeve, 4-electrical control cabinet, 5-bracket, 51-cover, 52-bottom support, 53-bottom plate, 60-Pump station, 601-Variable piston pump set, 602-Hydraulic oil tank, 61-cartridge overflow valve group, 62-cartridge overflow valve group, 63-second reversing valve, 64-first differential circuit, 641-cartridge overflow valve group, 642-first reversing valve, 643-cartridge proportional valve group, 65-auxiliary power source, 66-oil tank replenishing circuit, 661-high-level oil tank, 662-first cartridge valve, 67-first accumulator group, 68-second differential circuit, 681-check valve, 69-cartridge overflow valve group, 610-second accumulator group, 611-cartridge reversing valve group, 612-cartridge reversing valve group, 613-cartridge reversing valve group, 614-cartridge reversing valve group, 615-second cartridge valve, 71 - a first pressure sensor, 72 - a second pressure sensor, 73 - a third pressure sensor, 74 - a fourth pressure sensor, 75 - a fifth pressure sensor, 76 - a first displacement sensor, 77 - a second displacement sensor. DETAILED DESCRIPTION

[0031] The present invention is further described in detail below in conjunction with specific embodiments. However, this should not be understood as the scope of the above subject matter of the present invention being limited to the following embodiments, and all technologies realized based on the content of the present invention belong to the scope of the present invention.

[0032] Unless otherwise specified, in the description of the specific embodiments of the present invention, the terms indicating the orientation or position relationship such as "up", "down", "left", "right", "center", "inside", "outside", etc. are all expressions based on the orientation or position relationship shown in the drawings, or are the orientation or position relationship when the invented product / equipment / device is usually used. These terms of orientation or position relationship are only for the convenience of describing the scheme of the present invention or simplifying the description in the specific embodiments, so as to facilitate the technicians to quickly understand the scheme, and do not indicate or imply that a specific device / component / element must have a specific orientation, or be constructed and operated in a specific position relationship, and therefore cannot be understood as a limitation on the present invention.

[0033] In addition, if the terms "horizontal", "vertical", "overhanging", "parallel" and the like appear, it does not mean that the corresponding devices / components / elements are required to be absolutely horizontal or vertical or overhanging or parallel, but may be slightly tilted or have deviations. For example, "horizontal" only means that its direction is more horizontal than "vertical", and does not mean that the structure must be completely horizontal, but may be slightly tilted. Alternatively, it can be simplified to mean that the corresponding devices / components / elements are set in directions such as "horizontal", "vertical", "overhanging", "parallel", etc., and can have an error / deviation of ±10% relative to the corresponding direction setting, more preferably an error / deviation within ±8%, more preferably an error / deviation within ±6%, more preferably an error / deviation within ±5%, and more preferably an error / deviation within ±4%. As long as the corresponding device / component / element is within the error / deviation range, it can still achieve its role in the scheme of the present invention.

[0034] In addition, the expressions “first”, “second”, “third”, etc., which appear in the terms, are merely used to distinguish the description of the same or similar components and should not be understood as emphasizing or implying the relative importance of specific components.

[0035] In addition, in the description of the embodiments of the present invention, "several", "plurality" and "a number" represent at least 2. It can be any number such as 2, 3, 4, 5, 6, 7, 8, 9, and even more than 9.

[0036] In addition, in the description of the technical solution of the present invention, unless otherwise clearly specified / defined / restricted, the terms "set", "install", "connect", "connected", "provided with", "laid", and "arranged" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection, and can be welding, riveting, bolting, threading, and other commonly used connection means in the field. This connection can be a mechanical connection, an electrical connection, or a communication connection; it can be a direct connection, or an indirect connection through an intermediate medium, and it can be the internal connection of two elements.

[0037] Example 1 like Figure 1-Figure 4 As shown, a test device for testing the performance of a hydraulic gate hoist comprises a test cylinder 1, a loading cylinder 2, a hydraulic system and an electrical control cabinet 4; the test cylinder 1 and the loading cylinder 2 are supported by a bracket 5, are coaxially and horizontally arranged, the lower end cover of the test cylinder 1 and the upper end cover of the loading cylinder 2 are rigidly connected by a sleeve 3, and the piston rod of the test cylinder 1 and the piston rod of the loading cylinder 2 are rigidly connected in the sleeve 3; the hydraulic system comprises a pump station 60 and a control valve group, the pump station 60 comprises a variable piston pump group 601 and a hydraulic oil tank 602, the hydraulic system is connected to the test cylinder 1 and the loading cylinder 2 respectively, the electrical control cabinet 4 is used to control the action of the hydraulic system, adjust the interaction force between the test cylinder 1 and the loading cylinder 2, and simulate the load capacity of the fast hydraulic gate hoist under the test conditions, and the test conditions include any one of the door opening condition, the door closing condition and the accident door closing condition.

[0038] In one or several embodiments, the test cylinder 1 is a differentially connected double-acting hydraulic cylinder. The piston rod of the test cylinder 1 and the piston rod of the loading cylinder 2 are rigidly connected in the sleeve 3 by a coupling to ensure that the piston rod of the test cylinder 1 and the piston rod of the loading cylinder 2 have no rotational clearance when bearing load, and have high centering accuracy, can ensure accurate torque transmission, and can withstand large torque through the coupling to meet the high-load transmission simulation under large gate test conditions. The structure is simple and reliable, and the manufacturing and maintenance costs are low. At the same time, based on the characteristics of light weight, ultra-low inertia and high sensitivity of the coupling, it can meet the precise control of the movement of the test device under different test conditions, improve the test accuracy, and provide a test device for the hydraulic gate opening and closing machine that can meet the rapid opening and closing conditions.

[0039] In an optional embodiment, the outer diameters of the sleeve 3, the test cylinder 1 and the loading cylinder 2 are consistent, and the two ends of the sleeve 3 are connected to the lower end cover of the test cylinder 1 and the upper end cover of the loading cylinder 2 by bolts, forming an overall structure with consistent outer diameters including the test cylinder 1, the sleeve 3, and the loading cylinder 2. The combined structure of the test cylinder 1 and the loading cylinder 2 only includes an external stationary cylinder body part and an internal piston part that can reciprocate under the action of hydraulic oil. The test cylinder 1 and the loading cylinder 2 can be further connected as a whole, thereby avoiding external force interference during the test process to the greatest extent, avoiding possible unbalanced loading, ensuring accurate torque transmission of the piston rods of the two cylinders, and improving test accuracy.

[0040] like Figure 5As shown, in one or several embodiments, the pump station 60 includes several variable piston pump motor groups, the oil filling port of the pump station 60 is connected to the hydraulic oil tank 602, and the oil outlet of the pump station 60 can be connected to the test cylinder 1 and the loading cylinder 2 through a hydraulic pipeline including a door opening circuit, a door closing circuit or an emergency door closing circuit. The hydraulic pipeline is also connected to the hydraulic oil tank 602 for oil return. A shut-off valve and several control valve groups are provided on the hydraulic pipeline. Each shut-off valve and the control valve group are connected to the electrical control cabinet 4. The electrical control cabinet 4 controls the operation of the pump station 60 and the control valve group, so that the hydraulic pipeline can conduct the door opening circuit, the door closing circuit and the emergency door closing circuit respectively according to the test conditions.

[0041] In one or several embodiments, the control valve group includes a first cartridge reversing valve group 611, a second cartridge reversing valve group 612, a third cartridge reversing valve group 613, a fourth cartridge reversing valve group 614, a first reversing valve 642, a second reversing valve 63, a third cartridge overflow valve group 641, a first cartridge overflow valve group 61, a second cartridge overflow valve group 62, a fourth cartridge overflow valve group 69, a first cartridge valve 662, a second cartridge valve 615, a cartridge proportional valve group 643, and a one-way valve 681.

[0042] In an optional embodiment, if Figure 5 As shown, the first cartridge reversing valve group 611 is arranged between the pump station 60 and the rodless chamber 11 of the test cylinder, so that the pump station 60 can inject oil into the rodless chamber 11 of the test cylinder, and the rodless chamber 11 of the test cylinder can also return oil to the hydraulic oil tank 602; the second cartridge reversing valve group 612 is arranged between the pump station 60 and the rod chamber 12 of the test cylinder, the first cartridge reversing valve group 611 and the second cartridge reversing valve group 612 are connected to the first cartridge overflow valve group 61 after converging on the side close to the pump station 60, the first cartridge overflow valve group 61 is connected to the second reversing valve 63 and connected to the hydraulic oil tank 602, so that the pump station 60 can inject oil into the rod chamber 12 of the test cylinder, and the rodless chamber 11 of the test cylinder can also return oil to the hydraulic oil tank 602; The third cartridge relief valve group 641 and the cartridge proportional valve group 643 are arranged between the rod chamber 12 of the test cylinder and the rodless chamber 11 of the test cylinder. The third cartridge relief valve group 641 is connected to the first reversing valve 642, and the cartridge proportional valve group 643 is connected to the auxiliary power source 65, forming a first differential circuit 64; the one-way valve 681 is arranged between the rod chamber 12 of the test cylinder and the rodless chamber 11 of the test cylinder, forming a second differential circuit 68; so that the oil can be returned from the rod chamber 12 of the test cylinder to the rodless chamber 11 of the test cylinder under the action of the set flow rate and pressure, and the oil can also be returned from the rod chamber 12 of the test cylinder to the rodless chamber 11 of the test cylinder through the one-way valve 681; The third cartridge reversing valve group 613 is arranged between the pump station 60 and the rod chamber 21 of the loading cylinder. One end of the second cartridge relief valve group 62 is connected between the third cartridge reversing valve group 613 pump station 60 and the rod chamber 21 of the loading cylinder, and the other end is connected to the hydraulic oil tank 602. The second cartridge valve 615 is connected between the third cartridge reversing valve group 613 and the second cartridge relief valve group 62, so that the pump station 60 can inject oil into the rod chamber 21 of the loading cylinder, and the second cartridge relief valve group 62 can also adjust the load pressure of the rod chamber 21 of the loading cylinder; The fourth cartridge relief valve group 69 and the fourth cartridge reversing valve group 614 are arranged between the rodless chamber 22 of the loading cylinder and the hydraulic oil tank 602, so that the rodless chamber 22 of the loading cylinder can return oil to the hydraulic oil tank 602 at a set pressure, and the rodless chamber 22 of the loading cylinder can also be replenished with oil from the test oil tank; The first cartridge valve 662 is arranged on the oil tank oil replenishing circuit 66 connected to the rodless chamber 11 of the test cylinder, and is connected to the high-level oil tank 661, so that oil can be replenished from the high-level oil tank 661 to the rodless chamber 11 of the test cylinder.

[0043] In an optional embodiment, if Figure 3 As shown, part of the control valve group is integrated on the top of the hydraulic oil tank 602, such as Figure 4 As shown, part of the control valve group is concentrated near the outer end of the test cylinder 1.

[0044] like Figure 4 , Figure 5 As shown, by reasonably arranging the positions of each control valve group and combining the integrated setting of multiple plug-in reversing valve groups and plug-in overflow valve groups, the hydraulic system can achieve simultaneous adjustment of two cylinders through a single pump station and a set of integrated hydraulic pipelines. Each circuit can change the direction of the fluid flow according to actual conditions and share some pipelines. Compared with each cylinder being controlled by a hydraulic system separately, the integration of the hydraulic system can be achieved, the preparation cost of the test device can be reduced to the greatest extent, and the small volume and integrated control of the test device that meets the requirements of large flow and fast opening and closing can be achieved, the demand for test land can be reduced, and the distance between each control valve group can be reduced, which is convenient for centralized control, improves control precision, and thus improves test accuracy.

[0045] In one or more embodiments, a first accumulator group 67 is provided between the rod chamber 12 of the test cylinder and the pump station 60, and a second accumulator group 610 is provided between the rodless chamber 22 of the loading cylinder and the hydraulic oil tank 602. The first accumulator group 67 and the second accumulator group 610 are both a combination structure of an accumulator and a relief valve. Based on the characteristic that the accumulator can absorb and release energy by utilizing the compressibility of gas, when the system pressure increases, the hydraulic oil enters the accumulator and compresses the gas. When the system pressure drops, the gas expands and presses the hydraulic oil back into the system, thereby smoothing the pressure change, so that the test cylinder 1 and the loading cylinder 2 can be superimposed with the corresponding accumulator group under the corresponding working conditions, eliminating the output pulsation of the variable piston pump motor group, improving the pressure stability, and improving the test accuracy.

[0046] In an optional embodiment, the first accumulator group 67 and the second accumulator group 610 are arranged on both sides of the length direction of the combination, and the pump station 60 is provided with five variable piston pump motor groups and is arranged near the middle of the oil cylinder combination. This further realizes the reasonable centralized arrangement of the test device in the test site and improves the integration degree of the test device.

[0047] In one or more embodiments, the second reversing valve 63 includes a 1DT end electromagnet, the first cartridge reversing valve group 611 includes a 2DT end electromagnet, the cartridge proportional valve group 643 includes a 3DT end electromagnet, the first reversing valve 642 includes a 4DT end electromagnet, the second cartridge reversing valve group 612 includes a 5DT end electromagnet, the third cartridge reversing valve group 613 includes a 6DT end electromagnet, and the fourth cartridge reversing valve group 614 includes a 7DT end electromagnet; Figure 6 As shown, each electromagnet is energized under corresponding working conditions, where "+" represents energization.

[0048] Specifically, in the door opening condition, the electromagnet at the 1DT end, the electromagnet at the 5DT end and the electromagnet at the 7DT end are energized at the same time; in the door closing condition, the electromagnet at the 1DT end, the electromagnet at the 3DT end, the electromagnet at the 4DT end, the electromagnet at the 6DT end and the electromagnet at the 7DT end are energized at the same time; in the accident door closing condition, the electromagnet at the 1DT end, the electromagnet at the 2DT end and the electromagnet at the 3DT end are energized at the same time.

[0049] Specifically, During the door opening condition, the second cartridge reversing valve group 612 is opened, and the oil outlet of the pump station 60 is connected to the left position of the second cartridge reversing valve group 612 and the rod chamber 12 of the test cylinder. The overflow pressure at the outlet of the rod chamber 21 of the loading cylinder is adjusted by the second cartridge overflow valve group 62 to provide a suitable door opening load for the test cylinder 1, so that the piston rod of the test cylinder 1 is retracted.

[0050] In the closed-door working condition, the oil outlet of the pump station 60 is connected to the left position of the third cartridge reversing valve group 613 and the rod chamber 21 of the loading cylinder. At the same time, the first cartridge valve 662 is opened, and the rodless chamber 11 of the test cylinder and the oil outlet of the high-position oil tank 661 are connected through the oil tank replenishing circuit 66; at the same time, the first reversing valve 642 is energized, the cartridge proportional valve group 643 and the third cartridge overflow valve group 641 are opened, and the rod chamber 12 of the test cylinder and the rodless chamber 11 of the test cylinder are connected through the first differential circuit 64. The pressure of the rod chamber 12 of the test cylinder is stabilized by the first accumulator group 67 to ensure the stability of the closed-door working resistance, and the pressure at the outlet of the rod chamber 21 of the loading cylinder is appropriately adjusted by the second cartridge overflow valve group 62, so that the pressure of the rod chamber 21 of the loading cylinder reaches an equivalent load force, so that the piston rod of the test oil cylinder 1 extends from the end of the stroke.

[0051] In the accident closing condition, the first cartridge reversing valve group 611 is opened, and the oil outlet of the pump station 60 is connected to the left position of the first cartridge reversing valve group 611 and the rodless chamber 11 of the test cylinder. At the same time, the one-way valve 681 is opened to connect the rod chamber 12 of the test cylinder and the rodless chamber 11 of the test cylinder. The pressure of the rodless chamber 22 of the loading cylinder is stabilized by the second accumulator group 610 to ensure the stability of the accident closing load, and the pressure at the outlet of the rodless chamber 22 of the loading cylinder is adjusted by the fourth cartridge overflow valve group 69 to provide an equivalent back pressure load for the test cylinder 1, so that the piston rod of the test cylinder 1 extends from the end of the stroke.

[0052] In one or more embodiments, the rod chamber 12 of the test cylinder is connected to a first pressure sensor 71, the rodless chamber 11 of the test cylinder is connected to a second pressure sensor 72, the rod chamber 21 of the loading cylinder is connected to a third pressure sensor 73, the rodless chamber 22 of the loading cylinder is connected to a fourth pressure sensor 74, and the oil outlet of the pump station 60 is connected to a fifth pressure sensor 75, and all pressure sensors are respectively connected to the electrical control cabinet 4 for communication. This enables real-time collection of pressure data of each chamber under test conditions, so that accurate pressure adjustment of equivalent load can be performed through the electrical control cabinet 4, thereby improving the accuracy of the test.

[0053] In one or more embodiments, the rodless chamber 22 of the loading cylinder is connected to a first displacement sensor 76, and the rodless chamber 11 of the test cylinder is connected to a second displacement sensor 77, and the first displacement sensor 76 and the second displacement sensor 77 are respectively connected to the electrical control cabinet 4 for communication. This enables real-time acquisition of piston rod position data under test conditions, so that the pressure adjustment matching the opening and closing time of the rapid hydraulic hoist can be performed through the electrical control cabinet 4, further improving the accuracy of the test.

[0054] In one or more embodiments, Figure 2As shown, the bracket 5 includes a cover plate 51 and a bottom support 52, which are detachably connected to form a clamping channel that matches the appearance of the test cylinder 1, the loading cylinder 2 and the sleeve 3. A bottom plate 53 is provided at the bottom of the bottom support 52, and the bracket 5 is a steel structure. The test cylinder 1 and the loading cylinder 2 are stably supported to avoid vibration of the test device under the test condition, and to ensure that the tension and pressure between the test cylinder 1 and the loading cylinder 2 are the internal forces of the system of the test cylinder 1-sleeve 3-loading cylinder 2, thereby reducing the intervention of external forces in the system and improving the accuracy of the test.

[0055] In one or several embodiments, the electrical control cabinet 4 includes a manual control mode, which can select and set any test condition of the hydraulic hoist, perform simulation tests of any test condition, and collect and store data.

[0056] In one or more embodiments, the electrical control cabinet 4 includes a remote control mode, which can select and set any test condition of the hydraulic gate hoist or the interval between two adjacent test conditions through the host computer, perform a simulation test of any test condition or an automatic switching simulation test of multiple test conditions, and collect and store data. By remotely operating the host computer, not only can the test device work effectively and automatically, but it also has the ability to switch test conditions and collect and store data such as travel and pressure, which can greatly reduce manual labor intensity and save testing costs.

[0057] In an optional implementation, the electrical control cabinet 4 adopts PLC control technology. Through the design of the PLC control program, the manual control mode and the remote control mode can be switched on the control panel of the electrical control cabinet 4. The remote operation host computer has the ability to switch test conditions and collect and store data such as stroke and pressure, and can realize the effective and automatic operation of the test device, which can greatly reduce manual labor intensity and save testing costs.

[0058] The present embodiment is a test device for testing the performance of a hydraulic gate opening machine. In the door opening condition, the pump station 60 supplies oil to the rod chamber 12 of the test cylinder, the loading cylinder 2 provides a tensile force equivalent to the load to the test cylinder 1, and the piston rod of the test cylinder 1 retracts within the set door opening time; in the door closing condition, the pump station 60 supplies oil to the rod chamber 21 of the loading cylinder, the loading cylinder 2 provides a tensile force equivalent to the load to the test cylinder 1, and the piston rod of the test cylinder 1 extends within the set door closing time; in the accidental door closing condition, the pump station 60 supplies oil to the rodless chamber 11 of the test cylinder, the loading cylinder 2 provides a back pressure thrust equivalent to the load to the test cylinder 1, and the piston rod of the test cylinder 1 extends within the set door closing time.

[0059] A test device for testing the performance of a hydraulic gate hoist in the present embodiment obtains the combined force of gate gravity, water flow lifting force, water column force and friction resistance, etc., to which the rapid hydraulic gate hoist is actually subjected, based on physical experiments and simulation experiments in the early stage, to determine the gate opening force, gate closing force and accidental gate closing force required by the test device. By adopting the load equivalence principle, the gate gravity, water flow lifting force, water column force and friction resistance, etc., to which the rapid hydraulic gate hoist is actually subjected, are equivalent to the pulling force or thrust of the loading cylinder 2, and the gate opening time and gate closing time that meet the requirements of the rapid hydraulic gate hoist are set. The load capacity of the rapid hydraulic gate hoist under different test conditions can be simulated by adjusting a number of plug-in relief valve groups, so as to observe the various performances of the rapid hydraulic gate hoist. A test device that meets the requirements of the performance test of the rapid hydraulic gate hoist is provided, which has good operability, avoids the situation of using heavy objects to simulate gates, and reduces the test time. The overall volume of the test device; at the same time, in this embodiment, the test cylinder 1 and the loading cylinder 2 are combined to exceed 20 meters. By setting the test cylinder 1 and the loading cylinder 2 horizontally, the requirements for the site can be reduced, the performance test of a large-scale rapid hydraulic gate opening and closing machine can be met, the test cost can be saved, the test risk can be reduced, and the test operation can be more convenient; by rigidly connecting the test cylinder 1 and the loading cylinder 2 with a sleeve 3 of the same diameter, and rigidly connecting the piston rod of the test cylinder 1 and the piston rod of the loading cylinder 2 in the sleeve 3, the test cylinder 1 and the loading cylinder 2 become a whole, and the tension and pressure between the test cylinder 1 and the loading cylinder 2 become the internal force of the system of the overall structure, which can reduce the intervention of external forces in the system and improve the accuracy of the test. The performance indicators of the test device can also be observed through various pressure sensors and displacement sensors, thereby improving the accuracy and convenience of the test.

[0060] Example 2 Taking a test device for performance test of a large-scale ship lock rapid hydraulic hoist as an example, a test method for performance test of a hydraulic hoist is described. The maximum stroke of the large-scale ship lock rapid hydraulic hoist is 7m, the door opening time is 1min, the door closing time is 0.5m, and it is required to have a rapid door closing function in the event of an accident. The accident closing time is initially set to 1mmin, the door opening force is 3000KN, the door closing force is 400-600KN, the cylinder diameter is 480mm, and the piston rod diameter is 250mm. Due to the short door opening and closing time, fast speed and large working stroke of the hydraulic hoist, based on the existing technology, it is impossible to complete the accurate simulation of the door opening, door closing and accident closing conditions through a set of test devices. In order to realize the performance test of the door opening, door closing and accident closing conditions of the rapid hydraulic hoist, a test device for performance test of the hydraulic hoist as described above is proposed.

[0061] A test method for testing the performance of a hydraulic gate hoist comprises the following steps: S1. According to the test condition parameter requirements, a test device for testing the performance of a hydraulic gate hoist as described above is established; S2. Through the electrical control cabinet 4, simulate the door opening condition, door closing condition and accident door closing condition in manual control mode or remote control mode, and collect and store data.

[0062] In an optional implementation, establish Figure 4 The combination of the test cylinder 1 and the loading cylinder 2 shown in the figure rationally distributes various structural components and realizes rational utilization of the test site.

[0063] When the door is opened, the oil outlet of the variable piston pump motor group is connected to the oil inlet of the second cartridge reversing valve group 612, the oil outlet of the second cartridge reversing valve group 612 is connected to the rod chamber 12 of the test cylinder, the rodless chamber 11 of the test cylinder is connected to the hydraulic oil tank 602, the hydraulic oil tank 602 is connected to the oil inlet of the fourth cartridge reversing valve group 614, the rodless chamber 22 of the loading cylinder is connected to the oil outlet of the fourth cartridge reversing valve group 614, the rod chamber 21 of the loading cylinder is connected to the oil inlet of the cartridge relief valve group The oil outlet of the second cartridge relief valve group 62 is connected to the hydraulic oil tank 602, and five variable piston pump motor groups are started at no-load, with a delay of about five seconds to build up pressure in the hydraulic system. The electromagnet of the second reversing valve 63 is energized and then de-energized. The test cylinder 1 works at the set pressure of the fourth first cartridge relief valve group 61, and the pressure of the second cartridge relief valve group 62 at the outlet of the rod chamber 21 of the loading cylinder is adjusted to provide a suitable door opening load for the test cylinder 1, thereby realizing the load equivalence of the door opening condition.

[0064] In an optional implementation, the variable piston pump motor group of the pump station 60 can be adjusted according to actual conditions to ensure that the pressure requirements of the test device are met and appropriate backup is provided. For example, in the door opening condition, since the door opening load is relatively higher, the number of variable piston pump motor groups started synchronously can be increased accordingly to increase the total output flow of the pump station 60 and reduce the load corresponding to each variable piston pump motor group to avoid the problem of low system efficiency caused by overload of the variable piston pump motor group, so that the pump station 60 can work in a high-efficiency state and improve the reliability of the test device. Figure 6 As shown, the variable piston pump motor group of the pump station 60 can also be set to six units, in which "+" represents start and "-" represents shutdown.

[0065] In an optional implementation, the overflow pressure of the second cartridge overflow valve group 62 is manually debugged at the test site, and the maximum pressure of the second cartridge overflow valve group 62 is calculated based on the door-opening force, and then adjusted to build up pressure in the hydraulic system by adjusting the pressure of the second cartridge overflow valve group 62. In this embodiment, the door-opening force is 3000KN.

[0066] Specifically, the pressure P1 of the second plug-in relief valve group 62 = the door opening force F1 / the cylinder area A1.

[0067] In the closed-door working condition, the oil outlet of the variable piston pump motor group is connected to the oil inlet of the third cartridge reversing valve group 613, the oil outlet of the third cartridge reversing valve group 613 is connected to the rod chamber 21 of the loading cylinder, the rodless chamber 22 of the loading cylinder is connected to the oil inlet of the fourth cartridge reversing valve group 614, the oil outlet of the fourth cartridge reversing valve group 614 is connected to the hydraulic oil tank 602, the five variable piston pump motor groups are started, and the loading cylinder 2 works under the set pressure of the second cartridge relief valve group 62 , so that the pressure of the rod chamber 21 of the loading cylinder reaches the appropriate load force, adjust the pressure of the third plug-in relief valve group 641 at the outlet of the rod chamber 12 of the test cylinder, use the first accumulator group 67 to stabilize the pressure, and adjust the hydraulic pipeline connecting the hydraulic oil tank 4 and the rodless chamber 22 of the loading cylinder to make the rodless chamber 22 of the loading cylinder maintain sufficient back pressure thrust, which can truly simulate the water flow lifting force under the gate closing condition and provide the test cylinder 1 with a suitable closing load.

[0068] At the same time, the rod chamber 12 of the test cylinder is connected to the rodless chamber 11 of the test cylinder through the first differential circuit 64 composed of the cartridge proportional valve group 643, the third cartridge overflow valve group 641, and the first reversing valve 642. The valve core opening of the cartridge proportional valve group 643 is adjusted by the auxiliary power source 65 to control the reflux flow of the test cylinder 1, thereby realizing the buffering control of the test cylinder 1.

[0069] At the same time, the rodless chamber 11 of the test cylinder is connected to the oil outlet of the high-level oil tank 661 through the first cartridge valve 662 to supplement the insufficient hydraulic oil in the rodless chamber 11 of the test cylinder. It can quickly increase the flow of the rodless chamber 11 of the test cylinder and make the oil cylinder run faster to meet the rapid opening and closing requirements of the rapid hydraulic opening and closing machine.

[0070] In an optional embodiment, at the end of the stroke of the closed-door condition, the auxiliary power source 65 is driven by the electrical control cabinet 4 to continuously adjust the valve core opening of the plug-in proportional valve group 643, so that the valve core opening of the plug-in proportional valve group 643 is gradually reduced, so that the test cylinder 1 can obtain active and effective buffering control at the end of the closed-door condition, and in conjunction with the oil replenishment effect of the high-level oil tank 661, it can play an effective buffering role on the basis of meeting the short time requirement of the closed-door condition, avoid collision of the piston of the test cylinder 1, achieve stable closure of the gate, and further improve the test accuracy.

[0071] In an optional embodiment, the overflow pressure of the third cartridge overflow valve group 641 is manually debugged at the test site. By adjusting the pressure of the third cartridge overflow valve group 641 to reduce the set pressure of the third cartridge overflow valve group 641 or to increase the displacement of the variable piston pump motor group, a suitable closed-door load is provided to the test cylinder 1.

[0072] Specifically, the pressure P2 of the third plug-in relief valve group 641 = the closing force F2 / the cylinder area A2.

[0073] In the closed-door emergency condition, the oil outlet of the variable piston pump motor group is connected to the oil inlet of the first cartridge reversing valve group 611, the oil outlet of the first cartridge reversing valve group 611 is connected to the rodless chamber 11 of the test cylinder, the rod chamber 12 of the test cylinder is connected to the rodless chamber 11 of the test cylinder through the one-way valve 681, the rodless chamber 22 of the loading cylinder is connected to the oil inlet of the fourth cartridge relief valve group 69, the oil outlet of the fourth cartridge relief valve group 69 is connected to the hydraulic oil tank 602, and the second The oil inlet of the cartridge valve 615 is connected to the hydraulic oil tank 602, and the oil outlet of the second cartridge valve 615 is connected to the rod chamber 21 of the loading cylinder. The three variable piston pump motor groups are started, and the test cylinder 1 works at the set pressure of the first cartridge relief valve group 61. The pressure of the fourth cartridge relief valve group 69 at the outlet of the rodless chamber 22 of the loading cylinder is adjusted. At the same time, the second accumulator group 610 is used to stabilize the pressure and eliminate pressure pulsation, thereby providing an equivalent accident closed door load for the test cylinder 1.

[0074] At the same time, the rod chamber 12 of the test cylinder is connected to the rodless chamber 11 of the test cylinder through the one-way valve 681, and the buffer control of the test cylinder 1 is achieved by adjusting the output flow of the variable piston pump motor group.

[0075] At the same time, the rodless chamber 11 of the test cylinder is connected to the oil outlet of the variable piston pump motor group through the first plug-in reversing valve group 611. The insufficient hydraulic oil in the rodless chamber 11 of the test cylinder is supplemented by the variable piston pump motor group, so that the cylinder runs faster to meet the rapid opening and closing requirements of the rapid hydraulic opening and closing machine.

[0076] In an optional implementation, the pressure of the fourth plug-in relief valve group 69 is set according to the emergency closing force requirement and manually debugged at the test site. By adjusting the overflow pressure of the fourth plug-in relief valve group 69, an equivalent emergency closing load is provided for the test cylinder 1. In this embodiment, the emergency closing force is set to 400KN.

[0077] Specifically, the pressure P3 of the fourth plug-in relief valve group 69 = the emergency closing force F3 / the cylinder area A3.

[0078] In one or several embodiments, the test may be performed in a manual control mode or a remote control mode of the electrical control cabinet 4 .

[0079] In an optional embodiment, in the manual control mode, when it is necessary to open the door, long press the "open door" button on the electrical control cabinet 4, so that the second cartridge reversing valve group 612, the fourth cartridge reversing valve group 614, and the second reversing valve 63 are energized, and the door opening circuit starts to work, so that the high-pressure hydraulic oil flows to the rod chamber 12 of the test cylinder, thereby pushing the piston to move; when it is necessary to close the door, long press the "close door" button on the electrical control cabinet 4, so that the cartridge proportional valve group 643, the third cartridge overflow valve group 641, the third cartridge reversing valve group 613, the fourth cartridge reversing valve group 614, ... group When the directional valve 63 is energized, the closed-door circuit starts working, causing high-pressure oil to flow to the rod chamber 21 of the loading cylinder, thereby pushing the piston to move; when an emergency occurs and the door cannot be closed by relying on its own weight, long press the "accidental closed-door" button on the electrical control cabinet 4 to energize the first plug-in reversing valve group 611, the first reversing valve 642, and the second reversing valve 63, and the accident closed-door circuit starts working, causing high-pressure oil to flow to the rodless chamber 11 of the test cylinder, thereby pushing the piston to move. According to the actual situation, after repeating the door opening and door closing conditions for a certain number of times, the accident closed-door condition test can be carried out after the door opening condition.

[0080] In an optional implementation, in the remote control mode, by designing the PLC control program, the automatic opening and closing program can be started in the upper computer, so that the test cylinder 1 starts the door opening condition. After the door opening condition is completed, the hydraulic system automatically enters the pause stage. When the set pause time is over, the PLC restarts the automatic opening and closing program, drives the pump station 60 to build pressure, and executes the door closing condition action, thereby realizing continuous automatic operation of the door opening-door closing condition action and the door opening-accident door closing condition action. At the same time, the time interval between different test conditions can be set, and relevant data can be recorded.

[0081] A test method for testing the performance of a hydraulic gate hoist in the present embodiment, through the integrated control of the pump station 60 and the control valve group by the electrical control cabinet 4, can facilitate the effective operation of the test device under different test conditions, realize the true and accurate simulation of the door opening condition, door closing condition and accident door closing condition, reduce the manual labor intensity and save the test cost, and can improve the convenience of the test, and through the above-mentioned test device, realize the rapid and accurate response of the fast hydraulic gate hoist within the set door opening and closing time, thereby improving the accuracy of the test.

[0082] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. A test device for testing the performance of a hydraulic hoist, characterized in that: It comprises a test cylinder (1), a loading cylinder (2), a hydraulic system and an electrical control cabinet (4); The test cylinder (1) and the loading cylinder (2) are supported by a bracket (5) and are coaxially and horizontally arranged. The lower end cover of the test cylinder (1) and the upper end cover of the loading cylinder (2) are rigidly connected via a sleeve (3). The piston rod of the test cylinder (1) and the piston rod of the loading cylinder (2) are rigidly connected in the sleeve (3). The hydraulic system comprises a pump station (60) and a control valve group. The pump station (60) comprises a variable piston pump group (601) and a hydraulic oil tank (602). The hydraulic system is connected to the test cylinder (1) and the loading cylinder (2) respectively. The electrical control cabinet (4) is used to control the action of the hydraulic system, adjust the interaction force between the test cylinder (1) and the loading cylinder (2), and simulate the load capacity of the fast hydraulic hoist under the test working condition. The test working condition includes any one of the door opening working condition, the door closing working condition and the accident door closing working condition. In the door opening condition, the pump station (60) delivers oil to the rod chamber (12) of the test cylinder, the loading cylinder (2) provides a load-equivalent pulling force to the test cylinder (1), and the piston rod of the test cylinder (1) retracts within the set door opening time; In the closed door working condition, the pump station (60) delivers oil to the rod chamber (21) of the loading cylinder, the loading cylinder (2) provides a load-equivalent pulling force to the test cylinder (1), and the piston rod of the test cylinder (1) extends within the set closed door time; In the accidental door closing condition, the pump station (60) delivers oil to the rodless chamber (11) of the test cylinder, the loading cylinder (2) provides a load-equivalent back pressure thrust to the test cylinder (1), and the piston rod of the test cylinder (1) extends within the set door closing time.

2. A test device for testing the performance of a hydraulic gate hoist according to claim 1, characterized in that: In the door opening condition, the pump station (60) delivers oil to the rod chamber (12) of the test cylinder through the first plug-in overflow valve group (61); the first plug-in overflow valve group (61) is connected to the second reversing valve (63); the test oil cylinder (1) works under the set pressure of the first plug-in overflow valve group (61); the rodless chamber (11) of the test cylinder is connected to the hydraulic oil tank (602); the rod chamber (21) of the loading cylinder is connected to the return oil of the hydraulic oil tank (602) through the second plug-in overflow valve group (62); the hydraulic oil tank (602) is connected to the rodless chamber (22) of the loading cylinder for replenishing oil; and the load equivalence of the door opening condition can be achieved by adjusting the second plug-in overflow valve group (62).

3. A test device for testing the performance of a hydraulic gate hoist according to claim 2, characterized in that: In the closed-door working condition, the pump station (60) is connected to the rod chamber (21) of the loading cylinder, the loading cylinder (2) works under the set pressure of the second plug-in overflow valve group (62), and the rodless chamber (22) of the loading cylinder is connected to the return oil of the hydraulic oil tank (602); the rod chamber (12) of the test cylinder is connected to the rodless chamber (11) of the test cylinder through the first differential circuit (64), the first differential circuit (64) includes a third plug-in overflow valve group (641), the third plug-in overflow valve group (641) is connected to the first reversing valve (642), the rodless chamber (11) of the test cylinder is connected to the oil tank replenishing circuit (66), and the load equivalence of the closed-door working condition can be achieved by adjusting the third plug-in overflow valve group (641).

4. A test device for testing the performance of a hydraulic gate hoist according to claim 3, characterized in that: A first accumulator group (67) is provided between the rod chamber (12) of the test cylinder and the pump station (60). In a closed-door working condition, the pressure of the rod chamber (12) of the test cylinder is stabilized by the first accumulator group (67).

5. A test device for testing the performance of a hydraulic gate hoist according to claim 3, characterized in that: The first differential circuit (64) further comprises a plug-in proportional valve group (643), the plug-in proportional valve group (643) being arranged between the third plug-in relief valve group (641) and the rodless chamber (11) of the test cylinder, the plug-in proportional valve group (643) being connected to an auxiliary power source (65); in the closed-door working condition, the buffer control of the test oil cylinder (1) can be achieved by adjusting the plug-in proportional valve group (643).

6. A test device for testing the performance of a hydraulic gate hoist according to claim 3, characterized in that: The oil tank replenishing circuit (66) comprises a high-position oil tank (661) and a first cartridge valve (662); the high-position oil tank (661) is arranged on a side of the rodless chamber (11) close to the test cylinder; the high-temperature oil tank is arranged at a position higher than the test cylinder (1); and the high-position oil tank (661) is connected to a hydraulic oil tank (602) through a pipeline.

7. A test device for testing the performance of a hydraulic gate hoist according to claim 6, characterized in that: In the accident closed-door working condition, the pump station (60) is connected to the rodless chamber (11) of the test cylinder, and the rod chamber (12) of the test cylinder is connected to the rodless chamber (11) of the test cylinder through the second differential circuit (68). The test oil cylinder (1) works under the set pressure of the first plug-in overflow valve group (61); the rodless chamber (22) of the loading cylinder is connected to the return oil of the hydraulic oil tank (602) through the fourth plug-in overflow valve group (69), and the hydraulic oil tank (602) is connected to the rod chamber (21) of the loading cylinder for replenishing oil. The load equivalence of the accident closed-door working condition can be achieved by adjusting the fourth plug-in overflow valve group (69).

8. A test device for testing the performance of a hydraulic gate hoist according to claim 7, characterized in that: A second accumulator group (610) is provided between the rodless chamber (22) of the loading cylinder and the hydraulic oil tank (602). In an emergency door closing condition, the pressure of the rodless chamber (22) of the loading cylinder is stabilized by the second accumulator group (610).

9. A test device for testing the performance of a hydraulic hoist according to claim 7, characterized in that: The second differential circuit (68) includes a one-way valve (681). In the closed-door emergency condition, the rod chamber (12) of the test cylinder is connected to the rodless chamber (11) of the test cylinder through the one-way valve (681). The output flow of the pump station (60) is adjusted to achieve buffer control of the test oil cylinder (1).

10. A test device for testing the performance of a hydraulic gate hoist according to claim 7, characterized in that: A first cartridge reversing valve group (611) is provided between the pump station (60) and the rodless chamber (11) of the test cylinder, a second cartridge reversing valve group (612) is provided between the pump station (60) and the rod chamber (12) of the test cylinder, a third cartridge reversing valve group (613) is provided between the pump station (60) and the rod chamber (21) of the loading cylinder, and a fourth cartridge reversing valve group (614) is provided between the pump station (60) and the rodless chamber (22) of the loading cylinder; and a second cartridge valve (615) is provided between the hydraulic oil tank (602) and the rod chamber (21) of the loading cylinder.

11. A test device for testing the performance of a hydraulic gate hoist according to claim 10, characterized in that: The second reversing valve (63) includes a 1DT end electromagnet, the first plug-in reversing valve group (611) includes a 2DT end electromagnet, the plug-in proportional valve group (643) includes a 3DT end electromagnet, the first reversing valve (642) includes a 4DT end electromagnet, the second plug-in reversing valve group (612) includes a 5DT end electromagnet, the third plug-in reversing valve group (613) includes a 6DT end electromagnet, and the fourth plug-in reversing valve group (614) includes a 7DT end electromagnet; When the door is opened, the electromagnets at the 1DT end, 5DT end and 7DT end are energized at the same time; In the closed door condition, the electromagnets at the 1DT end, 3DT end, 4DT end, 6DT end and 7DT end are energized at the same time; In the accidental door closing condition, the electromagnet at the 1DT end, the electromagnet at the 2DT end and the electromagnet at the 3DT end are energized at the same time.

12. A test device for testing the performance of a hydraulic gate hoist according to any one of claims 1 to 11, characterized in that: The rod chamber (12) of the test cylinder is connected to a first pressure sensor (71), the rodless chamber (11) of the test cylinder is connected to a second pressure sensor (72), the rod chamber (21) of the loading cylinder is connected to a third pressure sensor (73), the rodless chamber (22) of the loading cylinder is connected to a fourth pressure sensor (74), and the oil outlet of the pump station (60) is connected to a fifth pressure sensor (75), and all the pressure sensors are respectively connected to the electrical control cabinet (4) for communication.

13. A test device for testing the performance of a hydraulic hoist according to claim 12, characterized in that: The rodless chamber (22) of the loading cylinder is connected to a first displacement sensor (76), and the rodless chamber (11) of the test cylinder is connected to a second displacement sensor (77). The first displacement sensor (76) and the second displacement sensor (77) are respectively connected to the electrical control cabinet (4) for communication.

14. A test device for testing the performance of a hydraulic hoist according to claim 11, characterized in that: The electrical control cabinet (4) includes a manual control mode, and the manual control mode can select and set any test working condition of the hydraulic gate hoist, perform a simulation test of any test working condition, and collect and store data.

15. A test device for testing the performance of a hydraulic hoist according to claim 11, characterized in that: The electrical control cabinet (4) includes a remote control mode, which can select and set any test condition of the hydraulic gate hoist or the interval between two adjacent test conditions through the host computer, perform a simulation test of any test condition or an automatic switching simulation test of multiple test conditions, and collect and store data.

16. A test device for testing the performance of a hydraulic hoist according to claim 11, characterized in that: The pump station (60) comprises a plurality of variable piston pump motor groups, and the number of variable piston pump motor groups started in any test condition is positively correlated with the opening and closing speed requirements and / or the opening and closing loads of the corresponding test condition.

17. A test device for testing the performance of a hydraulic hoist according to claim 11, characterized in that: The bracket (5) comprises a cover plate (51) and a bottom support (52). The cover plate (51) and the bottom support (52) are detachably connected to form a clamping channel that matches the appearance of the test cylinder (1), the loading cylinder (2) and the sleeve (3). A bottom plate (53) is provided at the bottom of the bottom support (52). The bracket (5) is a steel structure.

18. A test method for testing the performance of a hydraulic gate hoist, characterized in that: The steps include: S1. According to the test condition parameter requirements, establish a test device for testing the performance of a hydraulic gate hoist as described in any one of claims 1 to 17; S2. Through the electrical control cabinet (4), simulated tests of the door opening condition, the door closing condition and the door closing condition in an accident are respectively performed in a manual control mode or a remote control mode, and data are collected and stored.

19. A test method for testing the performance of a hydraulic gate hoist according to claim 18, characterized in that S2 include: S2.

1. Perform a door opening working condition test, supply oil to the rod chamber (12) of the test cylinder through the pump station (60), adjust the outlet pressure of the rod chamber (21) of the loading cylinder through the second plug-in relief valve group (62), so that the loading cylinder (2) provides a pulling force equivalent to the door opening load to the test cylinder (1); S2.2, conduct a closed-door working condition test, deliver oil to the rod chamber (21) of the loading cylinder through the pump station (60), adjust the outlet pressure of the rod chamber (21) of the loading cylinder through the second plug-in relief valve group (62), so that the rod chamber (21) of the loading cylinder reaches an equivalent load force, and replenish oil to the rodless chamber (11) of the test cylinder at a set pressure through the oil tank oil replenishment circuit (66) and the first differential circuit (64), so that the loading cylinder (2) provides a pulling force equivalent to the closed-door load to the test cylinder (1); S2.3, cycle S2.1-S2.2 several times; S2.

4. Perform an accident closed door working condition test. The pump station (60) delivers oil to the rodless chamber (11) of the test cylinder. The outlet pressure of the rodless chamber (22) of the loading cylinder is adjusted through the fourth plug-in relief valve group (69), so that the loading cylinder (2) provides a back pressure thrust equivalent to the accident closed door load to the test cylinder (1).

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