A test device and test method for hydraulic hoist performance test

Abstract

The present 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 hydraulic gate hoists. The test device comprises a test cylinder, a loading cylinder, a hydraulic system and an electrical control cabinet. By connecting the test cylinder and the loading cylinder into an integral whole, the tension and pressure between the test cylinder and the loading cylinder become the system internal force of the integral structure, reducing external force intervention and improving the accuracy of the test. At the same time, the load equivalence principle is adopted, and the opening and closing times 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, thereby observing the various performances of the rapid hydraulic gate hoist and providing a test device that meets the requirements of the performance test of the rapid hydraulic gate hoist. The test method controls the pump station and the control valve group through the electrical control cabinet, reduces manual labor intensity and saves test costs, and can improve the convenience of the test. The accuracy of the test is improved through the above-mentioned test device.

Description

Technical Field

[0001] The present 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 commonly used in water conservancy and hydropower projects. They generally consist of a hydraulic system and a hydraulic cylinder. Under the control of the hydraulic system, the piston in the hydraulic cylinder performs axial reciprocating motion along the inner wall, thereby driving the piston rod and the valve connected to the piston rod to perform linear reciprocating motion, thereby achieving the purpose of opening and closing the valve. Hydraulic gate hoists have very high reliability requirements. For valves with strict opening and closing time requirements, if the hydraulic gate hoist cannot complete opening or closing within the specified time, it will cause varying degrees of losses, 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, usually with a no-load test. The valve is opened or closed by the hydraulic gate hoist in the absence of 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 simply by conducting a no-load test on the hydraulic gate hoist, nor is it possible to judge the various performances of the hydraulic gate hoist in the fast 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 certain water conservancy hub. The filling and discharge steps are significantly increased compared with ordinary ship locks. The hub has a huge amount 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 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 gate. In addition, 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 gate 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 in 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;

[0007] 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;

[0008] 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.

[0009] During the door opening condition, the pump station delivers oil to the rod chamber of the test cylinder, and the loading cylinder provides a load-equivalent pulling force to the test cylinder. The piston rod of the test cylinder retracts within the set door opening time.

[0010] In the closed-door working condition, the pump station delivers oil to the rod chamber of the loading cylinder. The loading cylinder provides a load-equivalent pulling force to the test cylinder. The piston rod of the test cylinder extends within the set closed-door time.

[0011] During the accident 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. The piston rod of the test cylinder extends within the set closing time.

[0012] The test device for testing the performance 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 exerted on the rapid hydraulic gate hoist to the pulling force or thrust of the loading cylinder, and can set the gate opening time and closing time that meet the requirements of the rapid hydraulic gate hoist. It can simulate the load capacity of the rapid hydraulic gate hoist under different test conditions, thereby observing various performances of the rapid hydraulic gate hoist, and providing a test device that meets the requirements of the performance test of the rapid hydraulic gate hoist;

[0013] By setting the test cylinder and loading cylinder horizontally, the requirements for the site can be reduced to meet the performance test of large-scale rapid hydraulic hoists;

[0014] 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.

[0015] Preferably, during the door opening condition, the pump station supplies 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 to the hydraulic oil tank; the rod chamber of the loading cylinder is connected to the return oil of the hydraulic oil tank through the second cartridge overflow valve group, and the hydraulic oil tank is connected to the rodless chamber of the loading cylinder for oil replenishment, and adjusting the second cartridge overflow valve group can achieve load equivalence in the door opening condition.

[0016] The piston rod of the test cylinder is retracted to simulate the door opening working 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 working condition. In this way, the gate gravity, water flow lifting force, water column force and frictional resistance in the door closing working condition can be accurately simulated through accurate adjustment of the second plug-in relief valve group, providing accurate equivalent load force for the test cylinder and improving test accuracy.

[0017] Preferably, in the closed-door working condition, 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 overflow valve group, and the rodless chamber of the loading cylinder is connected to the return oil of the hydraulic oil 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 overflow valve group, the third cartridge overflow valve group is connected to the first reversing valve, and the rodless chamber of the test cylinder is connected to the oil tank oil replenishment circuit; adjusting the third cartridge overflow valve group can achieve load equivalence in the closed-door working condition.

[0018] The piston rod of the test oil cylinder is extended to simulate the closing working condition, and the pressure of the rod chamber of the loading cylinder is made to reach the appropriate load force through the second plug-in relief valve group. By adjusting the oil outlet pressure of the rod chamber of the test cylinder, the test oil cylinder is continuously provided with a pulling force equivalent to the closing working condition. In this way, the combination of the second plug-in relief valve group and the third plug-in relief valve group can accurately simulate the water flow lifting force, water column force and friction resistance in the closing working condition, provide the test oil cylinder with an accurate closing 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 rodless chamber flow of the test cylinder and make the cylinder run faster to meet the fast opening and closing requirements of the fast hydraulic gate opening and closing machine.

[0019] Preferably, a first accumulator group is provided between the rod chamber of the test cylinder and the pump station. In the closed-door working condition, the pressure of the rod chamber of the test cylinder is stabilized by the first accumulator group.

[0020] 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 the closed-door working condition, adjusting the cartridge proportional valve group can realize the buffering control of the test oil cylinder.

[0021] Preferably, the oil tank refill circuit includes a high-position oil tank and a first cartridge valve. The high-position oil tank is located near the rodless chamber of the test cylinder, and the high-temperature oil tank is located higher than the test cylinder. The high-position oil tank is connected to the hydraulic oil tank pipeline. This allows for rapid oil refilling of the rodless chamber of the test cylinder, enabling the test cylinder to meet the rapid opening and closing requirements of the rapid hydraulic hoist.

[0022] 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 oil cylinder works 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.

[0023] 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 accident closing working condition. The rodless cavity pressure of the loading cylinder is adjusted through the fourth plug-in relief valve group to provide the test cylinder with accurate accident closing back pressure load, further improving the test accuracy. The oil in the rod cavity of the test cylinder flows to the rodless cavity of the test cylinder through the second differential circuit, and the rodless cavity 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.

[0024] Preferably, a second accumulator group is provided between the rodless chamber of the loading cylinder and the hydraulic oil tank. In the emergency door closing working condition, the pressure of the rodless chamber of the loading cylinder is stabilized by the second accumulator group.

[0025] 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 realize buffer control of the test oil cylinder.

[0026] 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, and the fourth cartridge reversing valve group is provided between the pump station and the rodless chamber of the loading cylinder; and the second cartridge valve is provided between the hydraulic oil tank and the rod chamber of the loading cylinder. This enables control of the hydraulic oil circuit between the pump station and the test cylinder and the loading cylinder.

[0027] 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 closing condition, the 1DT end electromagnet, the 2DT end electromagnet and the 3DT end electromagnet are energized at the same time.

[0028] 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. All pressure sensors are respectively connected to the electrical control cabinet for communication. This enables real-time collection of pressure data from each chamber under test conditions, allowing accurate pressure adjustment of the equivalent load through the electrical control cabinet, thereby improving test accuracy.

[0029] Preferably, a first displacement sensor is connected to the rodless cavity of the loading cylinder, and a second displacement sensor is connected to the rodless cavity of the test cylinder. The first and second displacement sensors are each communicatively connected to an electrical control cabinet. This enables real-time acquisition of piston rod position data under test conditions, allowing pressure adjustment to match the opening and closing times of the rapid hydraulic hoist through the electrical control cabinet, further improving test accuracy.

[0030] Preferably, the electrical control cabinet 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.

[0031] Preferably, the electrical control cabinet includes a remote control mode. This mode enables the host computer to select and set any test condition of the hydraulic gate hoist or the interval between two adjacent test conditions, conduct a simulation test of any test condition or automatically switch between multiple test conditions, and collect and store data. Remote operation of the host computer not only enables the test device to operate effectively and automatically, but also provides the ability to switch test conditions and collect and store data such as stroke and pressure, which can greatly reduce manual labor intensity and save testing costs.

[0032] Preferably, the pump station includes several variable piston pump motor units. The number of variable piston pump motor units activated in any test condition is positively correlated with the required opening and closing speeds for that test condition. This allows the pump station to activate an appropriate number of variable piston pumps based on the test condition requirements, thereby meeting the test condition requirements and reducing the overall energy consumption of the test apparatus.

[0033] Preferably, the bracket includes a cover plate and a bottom support, which are detachably connected to form a clamping channel that adapts to the shape of the test cylinder, loading cylinder, and sleeve. The bottom of the bottom support is provided with a base plate, and the bracket is a steel structure. This provides stable support for the test cylinder and loading cylinder, preventing vibration of the test device under test conditions. It ensures that the tension and pressure between the test cylinder and loading cylinder are internal forces of the test cylinder-sleeve-loading cylinder system, reducing the interference of external forces in the system, thereby improving the accuracy of the test.

[0034] In a second aspect, the present invention provides a test method for testing the performance of a hydraulic hoist, comprising the following steps:

[0035] S1. Establish a test device for the performance test of a hydraulic gate hoist as described above according to the test condition parameter requirements;

[0036] S2. Through the electrical control cabinet, conduct simulation tests of door opening condition, door closing condition and accident door closing condition in manual control mode or remote control mode, and collect and store data.

[0037] The present invention provides a test method for testing the performance of a hydraulic gate hoist, which controls the action of a pump station and a control valve group through an electrical control cabinet, and 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, 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.

[0038] Preferably, S2 includes:

[0039] S2.1. Perform a door-opening operating condition test. Supply oil to the rod chamber of the test cylinder through the pump station. Adjust the rod chamber outlet pressure of the loading cylinder through the second cartridge relief valve assembly so that the loading cylinder applies a pulling force on the test cylinder equivalent to the door-opening load.

[0040] S2.2. Conduct a closed-door operating test. Use the pump station to deliver oil to the rod chamber of the loading cylinder. Use the second cartridge-type relief valve assembly to adjust the outlet pressure of the rod chamber of the loading cylinder to ensure that the rod chamber of the loading cylinder reaches an equivalent load. Use the tank oil supply circuit and the first differential circuit to supply oil to the rodless chamber of the test cylinder at a set pressure, ensuring that the loading cylinder applies a pulling force equivalent to the closed-door load to the test cylinder.

[0041] S2.3. Repeat S2.1-S2.2 several times;

[0042] S2.4. During the closed-door accident test, the pump station delivers oil to the rodless chamber of the test cylinder. The fourth cartridge-type relief valve group adjusts the rodless chamber outlet pressure of the loading cylinder, so that the loading cylinder provides a back pressure thrust equivalent to the closed-door accident load on the test cylinder. This ensures the effective and automatic operation of the test device.

[0043] Compared with the prior art, the present invention has the following beneficial effects:

[0044] 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 lift, water column force, and frictional resistance actually exerted on the rapid hydraulic gate hoist are equated to the pulling force or thrust of the loading cylinder. The gate opening and closing times are set to meet the requirements of the rapid hydraulic gate hoist. This device can simulate the load capacity of the rapid hydraulic gate hoist under different test conditions, thereby observing the various performance characteristics of the rapid hydraulic gate hoist. This provides a test device that meets the requirements of rapid hydraulic gate hoist performance testing.

[0045] 2. The present invention provides a test device for testing the performance of a hydraulic gate hoist. By arranging the test cylinder and the loading cylinder horizontally, the requirements for the site can be reduced, thus meeting the performance test requirements of large-scale rapid hydraulic gate hoists.

[0046] 3. The present invention provides a test device for testing the performance of a hydraulic gate hoist. By rigidly connecting a test cylinder and a loading cylinder using a sleeve, and rigidly connecting the piston rods of the test cylinder and the loading cylinder within the sleeve, the test cylinder and the loading cylinder become a single unit. The tension and pressure between the test cylinder and the loading cylinder become the internal forces of the system, which can reduce the interference of external forces in the system and improve the accuracy of the test.

[0047] 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 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

[0048] Figure 1 Schematic diagram of the structure of the test cylinder and the loading cylinder combination in Example 1;

[0049] Figure 2 for Figure 1 The schematic diagram of the partially enlarged structure at M in the middle;

[0050] Figure 3 This is a schematic structural diagram of the pump station in Example 1;

[0051] Figure 4 This is a schematic structural diagram of a test device for testing the performance of a hydraulic hoist according to Example 1;

[0052] Figure 5 A schematic diagram of a hydraulic system for a test device for testing the performance of a hydraulic gate hoist in Example 1;

[0053] Figure 6 The electrical operation diagram of the test device in Example 1 under different test conditions;

[0054] Figure 7 This is a control loop diagram for the manual control mode in Example 1;

[0055] Figure 8 This is the hardware configuration diagram of the electrical control cabinet;

[0056] Figure 9 This is the PLC configuration diagram of the electrical control cabinet;

[0057] Figure 10 This is a test data diagram of a large ship lock in the opening and closing conditions in Example 2;

[0058] Figure 11 This is a test data diagram of a large ship lock in Example 2 under the door opening-accident closing working conditions;

[0059] Markings in the figure:

[0060] 1-test cylinder, 11-rodless chamber of test cylinder, 12-rod chamber of test cylinder,

[0061] 2-loading cylinder, 21-loading cylinder rod chamber, 22-loading cylinder rodless chamber,

[0062] 3-sleeve, 4-electrical control cabinet, 5-bracket, 51-cover, 52-bottom support, 53-bottom plate,

[0063] 60-Pump station, 601-Variable piston pump group, 602-Hydraulic oil tank,

[0064] 61-Cartridge relief valve group, 62-Cartridge relief valve group, 63-Second reversing valve, 64-First differential circuit, 641-Cartridge relief valve group, 642-First reversing valve, 643-Cartridge proportional valve group, 65-Auxiliary power source, 66-Oil tank oil replenishment circuit, 661-High-level oil tank, 662-First cartridge valve, 67-First accumulator group, 68-Second differential circuit, 681-Check valve, 69-Cartridge relief 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,

[0065] 71 - first pressure sensor, 72 - second pressure sensor, 73 - third pressure sensor, 74 - fourth pressure sensor, 75 - fifth pressure sensor, 76 - first displacement sensor, 77 - second displacement sensor. DETAILED DESCRIPTION

[0066] The present invention will be further described in detail below with reference to specific embodiments. However, this should not be construed as limiting the scope of the present invention to the following embodiments, as all technologies implemented based on the present invention fall within the scope of the present invention.

[0067] Unless otherwise specified, in the description of the specific embodiments of the present invention, the terms indicating the orientation or positional relationship, such as "upper", "lower", "left", "right", "center", "inside", and "outside", are based on the expressions of the orientation or positional relationship shown in the accompanying drawings, or are the orientation or positional relationship in which the invented product / device / apparatus is placed when it is conventionally used. These terms of orientation or positional relationship are merely for the purpose of facilitating the description of the scheme of the present invention or simplifying the description of the specific embodiments to facilitate the rapid understanding of the scheme by technicians, 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 positional relationship, and therefore should not be understood as limiting the present invention.

[0068] 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 relative to "vertical", and does not mean that the structure must be completely horizontal, but may be slightly tilted. Alternatively, it can be simply understood that the corresponding devices / components / elements are set in directions such as "horizontal", "vertical", "overhanging", and "parallel", 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 solution of the present invention.

[0069] In addition, the expressions “first”, “second”, “third”, etc. 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.

[0070] In addition, in the description of the embodiments of the present invention, "several," "plurality," and "a number" represent at least two. It can also be any number such as two, three, four, five, six, seven, eight, nine, or even more than nine.

[0071] Furthermore, in the description of the technical solution of the present invention, unless otherwise expressly specified, defined, or limited, the terms "disposed," "installed," "connected," "connected," "provided with," "laid," and "arranged" should be understood broadly. For example, they may refer to fixed connections, detachable connections, or integral connections. They may be welded, riveted, bolted, threaded, or other commonly used connection methods in the art. Such connections may be mechanical, electrical, or communicative; they may be direct, indirect via an intermediate medium, or internally connected between two components.

[0072] Example 1

[0073] 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 plunger 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 working condition, and 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.

[0074] 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 through 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 precise 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 the hydraulic gate opening machine with a test device that can meet the rapid opening and closing conditions.

[0075] 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 the external stationary cylinder body part and the 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 into 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.

[0076] like Figure 5 As 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 an opening circuit, a closing circuit or an emergency closed 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 respectively conduct the opening circuit, the closing circuit and the emergency closed circuit according to the test conditions.

[0077] 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.

[0078] 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 fill the rodless chamber 11 of the test cylinder with oil, 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, and the first cartridge reversing valve group 611 and the second cartridge reversing valve group 612 are connected to the first cartridge relief valve group 61 after converging on the side close to the pump station 60. The first cartridge relief valve group 61 is connected to the second reversing valve 63 and is connected to the hydraulic oil tank 602, so that the pump station 60 can fill the rod chamber 12 of the test cylinder with oil, and the rodless chamber 11 of the test cylinder can also return oil to the hydraulic oil tank 602;

[0079] 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 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 a set flow rate and pressure, and 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;

[0080] The third cartridge reversing valve group 613 is disposed 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.

[0081] The fourth cartridge relief valve assembly 69 and the fourth cartridge reversing valve assembly 614 are disposed between the rodless chamber 22 of the loading cylinder and the hydraulic oil tank 602 , so that oil can be returned from the rodless chamber 22 of the loading cylinder to the hydraulic oil tank 602 at a set pressure, and oil can also be replenished from the test oil tank to the rodless chamber 22 of the loading cylinder;

[0082] 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.

[0083] 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, as shown in FIG. Figure 4 As shown, some control valve groups are concentrated near the outer end of the test cylinder 1.

[0084] like Figure 4 、 Figure 5As shown, by rationally arranging the positions of the control valve groups and combining the integrated setting of multiple plug-in reversing valve groups and plug-in relief 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 size 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 the control valve groups can be reduced, which facilitates centralized control, improves control precision, and thus improves test accuracy.

[0085] 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. Both the first accumulator group 67 and the second accumulator group 610 are combined structures of accumulators and relief valves. Based on the characteristic that accumulators can absorb and release energy by utilizing the compressibility of gas, when the system pressure increases, 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. Under the corresponding working conditions, the test cylinder 1 and the loading cylinder 2 work in conjunction with the corresponding accumulator groups, eliminating the output pulsation of the variable piston pump motor group, improving pressure stability, and thus improving test accuracy.

[0086] In an optional embodiment, the first accumulator group 67 and the second accumulator group 610 are located on either side of the assembly's length, and the pump station 60 is equipped with five variable displacement piston pump motors located near the center of the cylinder assembly. This further enables a rational centralized layout of the test equipment at the test site and improves the integration of the test equipment.

[0087] 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 the corresponding working conditions, where "+" represents energization.

[0088] Specifically, 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 emergency door closing condition, the 1DT end electromagnet, the 2DT end electromagnet and the 3DT end electromagnet are energized at the same time.

[0089] Specifically,

[0090] During the door opening condition, the second plug-in reversing valve group 612 is opened, and the oil outlet of the pump station 60 is connected to the left position of the second plug-in 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 plug-in 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.

[0091] During 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-level oil tank 661 are connected through the oil tank oil replenishment 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 is extended from the end of the stroke.

[0092] During the accident door 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 door 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.

[0093] 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. All pressure sensors are respectively connected to the electrical control cabinet 4. 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 4, thereby improving the accuracy of the test.

[0094] 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. The first displacement sensor 76 and the second displacement sensor 77 are respectively connected to the electrical control cabinet 4. This enables real-time acquisition of piston rod position data under test conditions, so that the electrical control cabinet 4 can adjust the pressure to match the opening and closing time of the rapid hydraulic hoist, further improving the accuracy of the test.

[0095] In one or more embodiments, Figure 2 As shown, bracket 5 comprises a cover plate 51 and a bottom support 52. The cover plate 51 and bottom support 52 are detachably connected to form a clamping channel that matches the external shapes of the test cylinder 1, loading cylinder 2, and sleeve 3. A bottom plate 53 is located at the bottom of the bottom support 52. Bracket 5 is a steel structure. This provides stable support for the test cylinder 1 and loading cylinder 2, preventing vibration of the test apparatus during testing. It ensures that the tension and compression between the test cylinder 1 and loading cylinder 2 are internal forces within the test cylinder 1-sleeve 3-loading cylinder 2 system, reducing external forces in the system and improving test accuracy.

[0096] In one or more 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.

[0097] In one or more embodiments, the electrical control cabinet 4 includes a remote control mode. This remote control mode enables the host computer to select and set any test condition of the hydraulic hoist or the interval between two adjacent test conditions, conduct a simulation test of any test condition or automatically switch between multiple test conditions, and collect and store data. Remote operation of the host computer not only enables the test device to operate effectively and automatically, but also provides the ability to switch test conditions and collect and store data such as stroke and pressure, which can greatly reduce manual labor intensity and save testing costs.

[0098] In an optional embodiment, 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.

[0099] The present embodiment provides a test device for testing the performance of a hydraulic door 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 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 door closing condition, the pump station 60 supplies 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 door closing time; in the accident closing condition, the pump station 60 supplies 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.

[0100] The present embodiment is a test device for testing the performance of a hydraulic gate hoist. In the early stage, the combined force of the gate gravity, water flow lifting force, water column force and friction resistance, etc., which the rapid hydraulic gate hoist actually receives, is obtained based on physical experiments and simulation experiments to determine the gate opening force, gate closing force and accident 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., which the rapid hydraulic gate hoist actually receives, are equivalent to the pulling force or pushing force 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 overflow 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 the 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.

[0101] Example 2

[0102] 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 working conditions through a set of test devices. In order to realize the performance test of the door opening, door closing and accident closing working conditions of the rapid hydraulic hoist, a test device for performance test of the hydraulic hoist as described above is proposed.

[0103] A test method for testing the performance of a hydraulic gate hoist comprises the following steps:

[0104] S1. Establish a test device for the performance test of a hydraulic gate hoist as described above according to the test condition parameter requirements;

[0105] 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.

[0106] In an optional embodiment, the following is established: Figure 4 The combination of the test cylinder 1 and the loading cylinder 2 shown rationally distributes various structural components and realizes rational utilization of the test site.

[0107] In the door opening condition, 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 plug-in relief valve group 62 is connected to the hydraulic oil tank 602, and the five variable piston pump motor groups are started at no load. The delay is 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 under the set pressure of the fourth first plug-in relief valve group 61, and the pressure of the second plug-in relief valve group 62 at the outlet of the rod chamber 21 of the loading cylinder is adjusted to provide the test cylinder 1 with a suitable door opening load, so as to achieve load equivalence of the door opening working condition.

[0108] In an optional embodiment, 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, where "+" represents start and "-" represents shutdown.

[0109] In an optional embodiment, the overflow pressure of the second plug-in overflow valve group 62 is manually debugged at the test site, and the maximum pressure of the second plug-in overflow valve group 62 is calculated based on the door opening force, and then adjusted to build pressure in the hydraulic system by adjusting the pressure of the second plug-in overflow valve group 62. In this embodiment, the door opening force is 3000KN.

[0110] Specifically, the pressure P1 of the second plug-in relief valve assembly 62 = the door opening force F1 / the cylinder area A1.

[0111] 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 overflow 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 by adjusting the hydraulic pipeline connecting the hydraulic oil tank 4 and the rodless chamber 22 of the loading cylinder, the rodless chamber 22 of the loading cylinder maintains 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.

[0112] 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 plug-in proportional valve group 643, the third plug-in overflow valve group 641, and the first reversing valve 642. The valve core opening of the plug-in 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.

[0113] 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 plug-in 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.

[0114] In an optional embodiment, at the end of the stroke of the closed-door working 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 gradually decreases, so that the test cylinder 1 can obtain active and effective buffering control at the end of the closed-door working condition, and cooperate with the oil replenishment effect of the high-level oil tank 661. On the basis of meeting the shorter time requirement of the closed-door working condition, it plays an effective buffering role, avoids collision of the piston of the test cylinder 1, realizes stable closure of the gate, and further improves the test accuracy.

[0115] In an optional embodiment, the overflow pressure of the third plug-in overflow valve group 641 is manually debugged at the test site. By adjusting the pressure of the third plug-in overflow valve group 641 to reduce the set pressure of the third plug-in overflow valve group 641 or increase the displacement of the variable plunger pump motor group, a suitable closing load is provided to the test cylinder 1.

[0116] Specifically, the pressure P2 of the third plug-in relief valve assembly 641 = the closing force F2 / the cylinder area A2.

[0117] 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 under 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, eliminate pressure pulsation, and provide an equivalent accident closed door load for the test cylinder 1.

[0118] 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.

[0119] At the same time, the rodless chamber 11 of the test cylinder is connected to the oil outlet of the variable plunger 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 plunger pump motor group, making the cylinder run faster to meet the rapid opening and closing requirements of the rapid hydraulic opening and closing machine.

[0120] In an optional embodiment, 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 to the test cylinder 1. In this embodiment, the emergency closing force is set to 400KN.

[0121] Specifically, the pressure P3 of the fourth plug-in relief valve assembly 69 = the emergency closing force F3 / the cylinder area A3.

[0122] 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 .

[0123] In an optional embodiment, in 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 relief valve group 641, the third cartridge reversing valve group 613, the fourth cartridge reversing valve group 614, the second reversing valve 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 door closing" 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 actual conditions, the door opening and closing conditions can be repeated a certain number of times, and then the accident closed-door condition test can be performed after the door opening condition.

[0124] In an optional implementation, in the remote control mode, through the design of 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 ends, the PLC restarts the automatic opening and closing program, drives the pump station 60 to perform pressure building operation, 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.

[0125] The test method for testing the performance of a hydraulic gate hoist in this embodiment can facilitate the effective operation of the test device under different test conditions by integrating the control pump station 60 and the control valve group through the electrical control cabinet 4, and realize the true and accurate simulation of the door opening condition, the door closing condition and the accident door closing condition, thereby reducing the labor intensity and saving the test cost, and improving 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 door opening and closing time, thereby improving the accuracy of the test.

[0126] 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 scope of protection of the present invention.

Claims

1. A test device for testing the performance of a hydraulic hoist, characterized in that: It includes a test oil cylinder (1), a loading oil 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 through 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 includes a pump station (60) and a control valve group. The pump station (60) includes 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. During the door opening operation, the pump station (60) delivers oil to the rod chamber (12) of the test oil cylinder, the loading oil cylinder (2) provides a load-equivalent pulling force to the test oil cylinder (1), and the piston rod of the test oil 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 accident closing condition, the pump station (60) delivers oil to the rodless chamber (11) of the test cylinder, and 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 closing time.

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

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

5. The test device for testing the performance of a hydraulic hoist according to claim 3, characterized in that: The first differential circuit (64) further includes a plug-in proportional valve group (643), which is arranged between the third plug-in relief valve group (641) and the rodless chamber (11) of the test oil cylinder. The plug-in proportional valve group (643) is connected to an auxiliary power source (65). When the door is closed, the plug-in proportional valve group (643) can be adjusted to achieve buffer control of the test oil cylinder (1).

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

7. A test device for testing the performance of a hydraulic 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 oil cylinder, and the rod chamber (12) of the test oil cylinder is connected to the rodless chamber (11) of the test oil 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 oil 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 oil cylinder for replenishing oil. By adjusting the fourth plug-in overflow valve group (69), load equivalence of the accident closed door working condition can be achieved.

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

9. The 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 operating condition, the rod chamber (12) of the test oil cylinder is connected to the rodless chamber (11) of the test oil cylinder through the one-way valve (681). Adjusting the output flow of the pump station (60) can achieve buffer control of the test oil cylinder (1).

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

11. A test device for testing the performance of a hydraulic 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 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 closed door working condition, the electromagnets at the 1DT end, 3DT end, 4DT end, 6DT end and 7DT end are energized at the same time; In the emergency 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 hoist according to any one of claims 1 to 11, characterized in that: The rod chamber (12) of the test oil cylinder is connected to a first pressure sensor (71), the rodless chamber (11) of the test oil cylinder is connected to a second pressure sensor (72), the rod chamber (21) of the loading oil cylinder is connected to a third pressure sensor (73), the rodless chamber (22) of the loading oil 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). All 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 oil cylinder is connected to a first displacement sensor (76), and the rodless chamber (11) of the test oil 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, which 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. The 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. The remote control mode 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) includes a plurality of variable piston pump motor groups, and the number of variable piston pump motor groups started in any test working condition is positively correlated with the opening and closing speed requirements and / or the opening and closing load of the corresponding test working condition.

17. The test device for testing the performance of a hydraulic hoist according to claim 11, characterized in that: The bracket (5) includes 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 is adapted to the outer shapes 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. Establishing a test device for testing the performance of a hydraulic gate hoist according to any one of claims 1 to 17 according to the test condition parameter requirements; S2. Through the electrical control cabinet (4), simulated tests of the door opening condition, door closing condition and accident door closing condition are respectively carried out 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 operating condition test. Oil is supplied to the rod chamber (12) of the test oil cylinder through the pump station (60). The outlet pressure of the rod chamber (21) of the loading oil cylinder is adjusted through the second plug-in relief valve group (62), so that the loading oil cylinder (2) provides a pulling force equivalent to the door opening load to the test oil cylinder (1). S2.2, conduct a closed-door working condition test, supply oil to the rod chamber (21) of the loading oil cylinder through the pump station (60), adjust the outlet pressure of the rod chamber (21) of the loading oil cylinder through the second plug-in relief valve group (62), so that the rod chamber (21) of the loading oil cylinder reaches an equivalent load force, and replenish oil to the rodless chamber (11) of the test oil cylinder at a set pressure through the oil tank oil replenishment circuit (66) and the first differential circuit (64), so that the loading oil cylinder (2) provides a pulling force equivalent to the closed-door load to the test oil cylinder (1); S2.

3. Repeat 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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