A dynamic loading hydraulic device for a hydraulic cylinder against lifting test bench

Abstract

The present invention discloses a dynamic loading hydraulic device for a hydraulic cylinder against a lifting test bench, and relates to the field of hydraulic loading for a capstan tensile test. The device comprises: one end of a hydraulic oil suction device is respectively connected to the first port of an electro-hydraulic reversing valve and the input port of a normally open electromagnetic overflow valve, and the other end and the other end of a first return path of hydraulic oil are both connected to a first oil tank; the output port of the normally open electromagnetic overflow valve is respectively connected to one end of the first return path of hydraulic oil and the second port of the electro-hydraulic reversing valve; one end of the first oil circuit is connected to the third port of the electro-hydraulic reversing valve, and the other end is connected to the rodless cavity of the hydraulic cylinder; one end of the second oil circuit is connected to the fourth port of the electro-hydraulic reversing valve, and the other end is respectively connected to one end of the third oil circuit and one end of the second return path of hydraulic oil; the other end of the third oil circuit is connected to the rod cavity of the hydraulic cylinder; and the other end of the second return path of hydraulic oil is connected to the second oil tank. The present invention improves the accuracy of the capstan pressure test results.

Description

Technical Field

[0001] The invention relates to the field of hydraulic loading for a capstan tensile test, and in particular to a dynamic loading hydraulic device for a hydraulic cylinder against a lifting test bench. Background Art

[0002] Capstans are crucial in power construction and cargo lifting at construction terminals, especially in the assembly of pole towers and hoisting and traction. Currently, when capstans are developed and shipped, they lack a dynamic load condition and a device that can timely detect their tension and wire rope speed. There are few hydraulic systems in the existing technology for dynamic loading resistance, and there is a lack of knowledge on how to use hydraulic cylinders to load lifting test benches, how to overcome the hydraulic system for tension testing, and how to ensure the stability of loading. Dynamic loading of hydraulic systems in capstan testing will cause a series of complex effects, including the generation of excess force, changes in system stability and response speed, and reduced control accuracy. Summary of the Invention

[0003] The purpose of the present invention is to provide a dynamic loading hydraulic device for a hydraulic cylinder against a lifting test bench, which can improve the accuracy of the pressure test results of a capstan grinder.

[0004] To achieve the above object, the present invention provides the following solutions:

[0005] A dynamic loading hydraulic device for a hydraulic cylinder antagonistic lifting test bench, comprising a hydraulic oil suction device, a normally open electromagnetic overflow valve, a first oil tank, a first hydraulic oil return path, an electro-hydraulic reversing valve, a hydraulic cylinder, a first oil path, a second oil path, a third oil path, a second hydraulic oil return path, and a steel wire rope;

[0006] One end of the hydraulic oil suction device is respectively connected to the first port of the electro-hydraulic reversing valve and the input port of the normally open electromagnetic relief valve; the output port of the normally open electromagnetic relief valve is respectively connected to one end of the first hydraulic oil return passage and the second port of the electro-hydraulic reversing valve; the other end of the hydraulic oil suction device and the other end of the first hydraulic oil return passage are both connected to the first oil tank;

[0007] The third port of the electro-hydraulic reversing valve is connected to one end of the first oil circuit; the other end of the first oil circuit is connected to the rodless chamber of the hydraulic cylinder;

[0008] The fourth port of the electro-hydraulic reversing valve is connected to one end of the second oil circuit; the other end of the second oil circuit is connected to one end of the third oil circuit and one end of the second hydraulic oil return passage respectively; the other end of the third oil circuit is connected to the rod chamber of the hydraulic cylinder; the other end of the second hydraulic oil return passage is connected to the second oil tank;

[0009] The hydraulic rod of the hydraulic cylinder is connected to the steel wire rope; the steel wire rope is connected to the capstan to be tested;

[0010] The working process of the hydraulic cylinder resisting the dynamic load of the capstan under test specifically includes:

[0011] The hydraulic oil suction device sucks hydraulic oil from the first oil tank and delivers the hydraulic oil to the normally open electromagnetic relief valve; the normally open electromagnetic relief valve returns the unloaded hydraulic oil in the hydraulic oil to the first oil tank through the first hydraulic oil return passage;

[0012] The above-mentioned capstan to be tested drives the hydraulic rod of the above-mentioned hydraulic cylinder to move through the above-mentioned wire rope, so that the target hydraulic oil in the above-mentioned rod chamber enters the above-mentioned hydraulic oil second return path through the above-mentioned third oil path; the above-mentioned normally open electromagnetic overflow valve transports the opposing hydraulic oil in the above-mentioned hydraulic oil to the above-mentioned second oil path through the above-mentioned electro-hydraulic reversing valve; the above-mentioned second oil path transports the above-mentioned opposing hydraulic oil to the above-mentioned hydraulic oil second return path; the above-mentioned hydraulic oil second return path transports the above-mentioned opposing hydraulic oil and the above-mentioned target hydraulic oil to the above-mentioned second oil tank; wherein, the pressure value set in the above-mentioned hydraulic oil second return path is the current load value of the above-mentioned hydraulic cylinder.

[0013] Optionally, the normally open electromagnetic relief valve includes a first pilot relief valve and a two-position two-way electromagnetic reversing valve;

[0014] The input end of the above-mentioned first pilot relief valve is respectively communicated with one end of the above-mentioned hydraulic oil suction device and the first port of the above-mentioned electro-hydraulic reversing valve; the output end of the above-mentioned first pilot relief valve is respectively communicated with one end of the above-mentioned hydraulic oil first return passage and the second port of the above-mentioned electro-hydraulic reversing valve; the control oil outlet of the above-mentioned first pilot relief valve is communicated with the first port of the above-mentioned two-position two-way solenoid reversing valve; the second port of the above-mentioned two-position two-way solenoid reversing valve is communicated with one end of the above-mentioned hydraulic oil first return passage.

[0015] Optionally, the electro-hydraulic directional control valve includes a hydraulic directional control valve and a three-position four-way electromagnetic directional control valve;

[0016] The first port of the above-mentioned hydraulic reversing valve is connected to one end of the above-mentioned first oil circuit; the second port of the above-mentioned hydraulic reversing valve is connected to one end of the above-mentioned second oil circuit; the third port of the above-mentioned hydraulic reversing valve is connected to the third port of the above-mentioned three-position four-way solenoid reversing valve; the fourth port of the above-mentioned hydraulic reversing valve is connected to the fourth port of the above-mentioned three-position four-way solenoid reversing valve; the first port of the above-mentioned three-position four-way solenoid reversing valve is connected to the second pressure oil inlet of the above-mentioned hydraulic reversing valve; the second port of the above-mentioned three-position four-way solenoid reversing valve is connected to the first pressure oil inlet of the above-mentioned hydraulic reversing valve; the third port of the above-mentioned three-position four-way solenoid reversing valve is connected to the input port of the above-mentioned normally open electromagnetic overflow valve; the fourth port of the above-mentioned three-position four-way solenoid reversing valve is connected to the output port of the above-mentioned normally open electromagnetic overflow valve.

[0017] Optionally, the second hydraulic oil return passage includes a second pilot relief valve and a second pressure sensor;

[0018] One end of the second pilot relief valve is connected to the other end of the second oil circuit; the other end of the second pilot relief valve is connected to the second oil tank;

[0019] The second pressure sensor is connected to one end of the second pilot relief valve; the second pressure sensor is used to detect the pressure of the hydraulic oil flowing into the second pilot relief valve; the hydraulic oil flowing into the second pilot relief valve includes the target hydraulic oil and the opposing hydraulic oil.

[0020] Optionally, the second oil circuit includes a second one-way valve;

[0021] One end of the second one-way valve is communicated with the fourth port of the electro-hydraulic reversing valve; the other end of the second one-way valve is communicated with one end of the third oil circuit.

[0022] Optionally, the first oil circuit includes a throttle valve and a first stop ball valve;

[0023] One end of the throttle valve is connected to the third port of the electro-hydraulic reversing valve; the other end of the throttle valve is connected to one end of the first stop ball valve; the other end of the first stop ball valve is connected to the rodless chamber of the hydraulic cylinder.

[0024] Optionally, the third oil circuit includes a second stop ball valve;

[0025] One end of the second stop ball valve is communicated with the other end of the second oil circuit; the other end of the second stop ball valve is communicated with the rod chamber of the hydraulic cylinder.

[0026] Optionally, the hydraulic oil first return path includes a cooler, a fan and a flow sensor;

[0027] One end of the cooler is connected to the output port of the normally open electromagnetic relief valve;

[0028] The fan is used to accelerate the cooling speed of the cooler;

[0029] The other end of the cooler is connected to one end of the flow sensor;

[0030] The other end of the flow sensor is communicated with the first oil tank.

[0031] Optionally, the hydraulic oil suction device includes a filter, an oil pump motor, an oil pump, a first one-way valve and a first pressure sensor;

[0032] One end of the filter is connected to the first oil tank; the other end of the filter is connected to one end of the oil pump; the other end of the oil pump is connected to one end of the first one-way valve; the other end of the first one-way valve is connected to the input port of the normally open electromagnetic relief valve;

[0033] The first pressure sensor is connected to the input port of the normally open electromagnetic relief valve;

[0034] The oil pump motor is connected to the oil pump; the oil pump motor is used to drive the oil pump to work.

[0035] Optionally, the above device further includes a temperature sensor;

[0036] The temperature sensor is used to detect the temperature of the hydraulic oil in the first oil tank.

[0037] According to the specific embodiments provided by the present invention, the present invention discloses the following technical effects:

[0038] The present invention discloses a dynamic loading hydraulic device for a hydraulic cylinder anti-lifting test bench. When the wire rope of a capstan pulls the hydraulic cylinder, the hydraulic cylinder is in an anti-lifting working state. At this time, the electro-hydraulic reversing valve is de-energized and in the middle position. The normally open electromagnetic overflow valve is de-energized to achieve system pressure relief. Since the second oil circuit is a one-way flow, the oil in the rod chamber of the hydraulic cylinder can only be controlled by the return flow through the second return path of the hydraulic oil. As the tension of the wire rope changes, the process of anti-lifting of the hydraulic system can be achieved by adjusting the pressure of the second return path of the hydraulic oil. When the wire rope is actively lowered, the electro-hydraulic reversing valve is energized and works in the left position. The normally open electromagnetic overflow valve is energized to establish system pressure. At this time, the hydraulic cylinder is in a coordinated free-falling state. The present invention can be applied to the tension test of a new type of capstan, and can detect its tension and wire rope speed under dynamic load conditions. It overcomes the influence of the hydraulic system on the tension test results and realizes the functions of anti-lifting and coordinated free-fall. BRIEF DESCRIPTION OF THE DRAWINGS

[0039] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0040] Figure 1 A schematic structural diagram of a dynamic loading hydraulic device of a hydraulic cylinder anti-lifting test bench provided in Example 1 of the present invention;

[0041] Figure 2 Schematic diagram of the working process of the dynamic loading hydraulic device of the hydraulic cylinder anti-lifting test bench provided in Example 1 of the present invention.

[0042] Figure 3 Schematic diagram of an application scenario of a dynamic loading hydraulic device for a hydraulic cylinder anti-lifting test bench provided in Example 1 of the present invention;

[0043] Figure 4 This is a schematic diagram of the overall structure of the dynamic loading hydraulic device of the hydraulic cylinder anti-lifting test bench provided in Example 1 of the present invention.

[0044] Explanation of symbols:

[0045] 1: First oil tank; 2: Filter; 3: Temperature sensor; 4: Flow sensor; 5: Cooler; 6: Fan; 7: Oil pump motor; 8: Oil pump; 9: First check valve; 10: Two-position, two-way solenoid directional valve; 11: First pilot relief valve; 12: First pressure sensor; 13: Three-position, four-way solenoid directional valve; 13-1: Left electromagnet; 13-2: Right electromagnet; 14: Hydraulic reversing valve; 15: Second oil tank; 16: Second pilot relief valve; 17: Throttle valve; 18: Second check valve; 19: Second pressure sensor; 20: First stop ball valve; 21: Second stop ball valve; 22: Hydraulic cylinder; 22-1: Rod chamber; 22-2: Hydraulic rod; 22-3: Piston ;22-4: Rodless cavity;23: Wire rope;24: Pipeline;24-1: Pipeline one;24-2: Pipeline two;24-3: Pipeline three;24-4: Pipeline four;24-5: Pipeline five;24-6: Pipeline six;24-7: Pipeline seven;24-8: Pipeline eight;24-9: Pipeline nine;24-10: Pipeline ten;24-11: Pipeline eleven;24-12: Pipeline twelve;24-13: Pipeline thirteen;24-14: Pipeline fourteen;24-15: Pipeline fifteen;24-16: Pipeline sixteen;24-17: Pipeline seventeen;24-18: Pipeline eighteen;24-19: Pipeline nineteen;24-20: Pipeline twenty;24-21: Pipeline twenty-one. DETAILED DESCRIPTION

[0046] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0047] The object of the present invention is to provide a dynamic loading hydraulic device for a hydraulic cylinder 22 against a lifting test bench, in order to improve the accuracy of the pressure test results of a capstan grinder.

[0048] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments.

[0049] Example 1

[0050] like Figure 1 、 Figure 3 and Figure 4 As shown, in this embodiment, a hydraulic device for a hydraulic cylinder 22 resisting dynamic loading of a lifting test bench includes: a hydraulic oil suction device, a normally open electromagnetic relief valve, a first oil tank 1, a first hydraulic oil return path, an electro-hydraulic reversing valve, a hydraulic cylinder 22, a first oil circuit, a second oil circuit, a third oil circuit, a second hydraulic oil return path, and a steel wire rope 23. The hydraulic oil suction device, the normally open electromagnetic relief valve, the first oil tank 1, the first hydraulic oil return path, the electro-hydraulic reversing valve, the hydraulic cylinder 22, the first oil circuit, the second oil circuit, the third oil circuit, the second hydraulic oil return path, and the steel wire rope 23 are all connected via a pipeline 24.

[0051] One end of the hydraulic oil suction device is connected to the first port of the electro-hydraulic reversing valve and the input port of the normally open electromagnetic relief valve, respectively. The output port of the normally open electromagnetic relief valve is connected to one end of the first hydraulic oil return path and the second port of the electro-hydraulic reversing valve, respectively. The other end of the hydraulic oil suction device and the other end of the first hydraulic oil return path are both connected to the first oil tank 1. The hydraulic oil suction device is used to draw hydraulic oil from the first oil tank and deliver it to the input port of the normally open electromagnetic relief valve.

[0052] The third port of the electro-hydraulic reversing valve is communicated with one end of the first oil circuit; the other end of the first oil circuit is communicated with the rodless chamber 22 - 4 of the hydraulic cylinder 22 .

[0053] The fourth port of the electro-hydraulic reversing valve is connected to one end of the second oil circuit; the other end of the second oil circuit is respectively connected to one end of the third oil circuit and one end of the second return passage of hydraulic oil; the other end of the third oil circuit is connected to the rod chamber 22-1 of the hydraulic cylinder 22; the other end of the second return passage of hydraulic oil is connected to the second oil tank 15.

[0054] The hydraulic rod 22 - 2 of the hydraulic cylinder 22 is connected to the steel wire rope 23 ; the steel wire rope 23 is connected to the capstan to be tested.

[0055] The hydraulic cylinder 22 includes a rod chamber 22 - 1 , a hydraulic rod 22 - 2 , a piston 22 - 3 , and a rodless chamber 22 - 4 .

[0056] As a specific embodiment, the normally open electromagnetic relief valve includes a first pilot relief valve 11 and a two-position two-way electromagnetic reversing valve 10. When de-energized, the normally open electromagnetic relief valve is in a normally open state, which can reduce the pressure of the hydraulic cylinder 22 against the dynamic loading hydraulic device of the lifting test bench.

[0057] The input end of the first pilot relief valve 11 is connected to one end of the hydraulic oil suction device and the first port of the electro-hydraulic reversing valve respectively; the output end of the first pilot relief valve 11 is connected to one end of the first return passage of hydraulic oil and the second port of the electro-hydraulic reversing valve respectively; the control oil outlet of the first pilot relief valve 11 is connected to the first port of the two-position two-way solenoid reversing valve 10; the second port of the two-position two-way solenoid reversing valve 10 is connected to one end of the first return passage of hydraulic oil.

[0058] As a specific embodiment, the electro-hydraulic directional control valve includes a hydraulic directional control valve 14 and a three-position, four-way electromagnetic directional control valve 13. The three-position, four-way electromagnetic directional control valve 13 includes a left electromagnet 13-1 and a right electromagnet 13-2. Corresponding to the different energization states of the two electromagnets, the three-position, four-way electromagnetic directional control valve 13 has three different working positions: left, center, and right. When both the left electromagnet 13-1 and the right electromagnet 13-2 are de-energized, the three-position, four-way electromagnetic directional control valve 13 is in the center working state.

[0059] The first port of the hydraulic reversing valve 14 is connected to one end of the first oil circuit; the second port of the hydraulic reversing valve 14 is connected to one end of the second oil circuit; the third port of the hydraulic reversing valve 14 is connected to the third port of the three-position four-way solenoid reversing valve 13; the fourth port of the hydraulic reversing valve 14 is connected to the fourth port of the three-position four-way solenoid reversing valve 13; the first port of the three-position four-way solenoid reversing valve 13 is connected to the second pressure oil inlet of the hydraulic reversing valve 14; the second port of the three-position four-way solenoid reversing valve 13 is connected to the first pressure oil inlet of the hydraulic reversing valve 14; the third port of the three-position four-way solenoid reversing valve 13 is connected to the input port of the normally open electromagnetic overflow valve; the fourth port of the three-position four-way solenoid reversing valve 13 is connected to the output port of the normally open electromagnetic overflow valve.

[0060] As a specific embodiment, the second hydraulic oil return passage includes a second pilot relief valve 16 and a second pressure sensor 19 .

[0061] One end of the second pilot relief valve 16 is connected to the other end of the second oil circuit; the other end of the second pilot relief valve 16 is connected to the second oil tank 15 through pipeline 18 24-18.

[0062] The second pressure sensor 19 is connected to one end of the second pilot relief valve 16 through pipeline sixteen 24-16; the second pressure sensor 19 is used to detect the pressure of the hydraulic oil flowing into the second pilot relief valve 16; the hydraulic oil flowing into the second pilot relief valve 16 includes target hydraulic oil and opposing hydraulic oil.

[0063] As a specific embodiment, the second oil circuit includes a second one-way valve 18. One end of the second one-way valve 18 is connected to the fourth port of the electro-hydraulic reversing valve; the other end of the second one-way valve 18 is connected to one end of the third oil circuit.

[0064] As a specific implementation, the first oil circuit includes a throttle valve 17 and a first stop ball valve 20; one end of the throttle valve 17 is connected to the third port of the electro-hydraulic reversing valve; the other end of the throttle valve 17 is connected to one end of the first stop ball valve 20; the other end of the first stop ball valve 20 is connected to the rodless chamber 22-4 of the hydraulic cylinder 22.

[0065] As a specific embodiment, the third oil circuit includes a second cut-off ball valve 21 ; one end of the second cut-off ball valve 21 is connected to the other end of the second oil circuit; the other end of the second cut-off ball valve 21 is connected to the rod chamber 22 - 1 of the hydraulic cylinder 22 .

[0066] As a specific implementation, the first return path of the hydraulic oil includes a cooler 5, a fan 6 and a flow sensor 4; one end of the cooler 5 is connected to the output port of the normally open electromagnetic overflow valve; the fan 6 is used to accelerate the cooling speed of the cooler 5; the other end of the cooler 5 is connected to one end of the flow sensor 4; the other end of the flow sensor 4 is connected to the first oil tank 1.

[0067] As a specific embodiment, the hydraulic oil suction device includes a filter 2, an oil pump motor 7, an oil pump 8, a first one-way valve 9 and a first pressure sensor 12; one end of the filter 2 is connected to the first oil tank 1; the other end of the filter 2 is connected to one end of the oil pump 8; the other end of the oil pump 8 is connected to one end of the first one-way valve 9; the other end of the first one-way valve 9 is connected to the input port of the normally open electromagnetic overflow valve; the first pressure sensor 12 is connected to the input port of the normally open electromagnetic overflow valve through pipeline five 24-5; the oil pump motor 7 is connected to the oil pump 8; the oil pump motor 7 is used to drive the oil pump 8 to work.

[0068] As a specific embodiment, the device further includes a temperature sensor 3 ; the temperature sensor 3 is used to detect the temperature of the hydraulic oil in the first oil tank 1 .

[0069] like Figure 2 As shown, the working process of the hydraulic cylinder 22 against the dynamic load of the capstan to be tested specifically includes:

[0070] The hydraulic oil suction device sucks hydraulic oil from the first oil tank 1 and delivers the hydraulic oil to the normally open electromagnetic overflow valve; the normally open electromagnetic overflow valve returns the unloaded hydraulic oil in the hydraulic oil to the first oil tank 1 through the hydraulic oil first return path; this process is a low-pressure bypass cycle.

[0071] As a specific implementation process, the working process of the low-pressure bypass cycle can be:

[0072] The oil pump 8 draws hydraulic oil from the first oil tank 1. The hydraulic oil first passes through the filter 2 from pipeline 1 24-1 and then is sucked into the oil pump 8 from pipeline 2 24-2. Then, the hydraulic oil passes through the first one-way valve 9 from pipeline 3 24-3, pipeline 4 24-4, pipeline 6 24-6 directly through the first pilot relief valve 11, and then through pipeline 7 24-7, pipeline 10 24-10, cooler 5, pipeline 11 24-11, flow sensor 4, pipeline 12 24-12 and flows back to the first oil tank 1, realizing low-pressure unloading of the system.

[0073] The capstan under test drives the hydraulic rod 22-2 of the hydraulic cylinder 22 via the steel wire rope 23, causing the target hydraulic oil in the rod chamber 22-1 to enter the second hydraulic oil return path through the third oil circuit. The normally open electromagnetic relief valve transfers the opposing hydraulic oil in the hydraulic oil to the second oil circuit via the electro-hydraulic reversing valve. The second oil circuit then transfers the opposing hydraulic oil to the second hydraulic oil return path. The second hydraulic oil return path then transfers the opposing hydraulic oil and the target hydraulic oil to the second oil tank 15. The pressure set in the second hydraulic oil return path is the current load value of the hydraulic cylinder 22. This process is a high-pressure working circuit.

[0074] As a specific implementation process, the working process of the high-voltage working circuit can be:

[0075] During the process of lifting the winch grinder to be tested by the hydraulic cylinder 22, oil is sucked in from the pipeline thirteen 24-13 through the T port of the Y-type reversing valve, and passes through the pipeline fourteen 24-14 through the second one-way valve 18. Due to the one-way flow characteristics of the second one-way valve 18, the oil passing through the electro-hydraulic reversing valve and the hydraulic cylinder 22 can only flow back to the second oil tank 15 through the pipeline nineteen 24-19 and the pipeline seventeen 24-17 through the second pilot relief valve 16. At this time, the pressure set by the second pilot relief valve 16 reflects the current load value of the hydraulic cylinder 22, thereby realizing the dynamic load operation of the hydraulic cylinder 22 against the lifting test bench.

[0076] The above process is the lifting process of the capstan to be tested. At this time, the hydraulic cylinder 22 is in the working state of the anti-hydraulic system. At this time, the normally open electromagnetic overflow valve in the system is in the open state because it is not energized, thereby realizing system pressure relief. At the same time, the left electromagnet 13-1 and the right electromagnet 13-2 of the electromagnetic reversing valve are not energized and are in the neutral working state.

[0077] When the hydraulic loading device is in the free-falling working state in coordination with the hydraulic cylinder 22, the hydraulic cylinder 22 actively releases the pressure and drives the piston 22-3 rod to descend. At this time, the normally open electromagnetic overflow valve is connected to the power supply to establish the system pressure. At the same time, the left electromagnet 13-1 of the electromagnetic reversing valve is energized, so that the electromagnetic reversing valve is in the left working state. The rod chamber 22-1 of the hydraulic cylinder 22 receives the high-pressure oil from the electromagnetic reversing valve B port through the pipeline 14 24-14, the second one-way valve 18, the pipeline 15 24-15, the second stop ball valve 21 and the pipeline 19 24-19 into the rod chamber 22-1 of the hydraulic cylinder 22 as the driving force, while the rodless chamber 2 2-4 is connected to the low-pressure area, and the oil flows from the rodless chamber 22-4 through pipeline 20 24-20, the first stop ball valve 20, the throttle valve 17, pipeline 21 24-21, the P port of the electro-hydraulic reversing valve, pipeline 6 24-6, pipeline 8 24-8, pipeline 9 24-9, pipeline 10 24-10, through the cooler 5, pipeline 11 24-11, the flow sensor 4, and pipeline 12 24-12 back to the first oil tank 1, forming a pressure difference to cause the piston 22-3 rod to descend smoothly.

[0078] The maximum load tested by the present invention is not less than 80% of the maximum working load of the equipment. The hydraulic cylinder 22 is an HSG125×1000 single-rod engineering hydraulic cylinder 22, the hydraulic rod 22-2 has a rod diameter D=125mm, a rod diameter d=70mm, a hydraulic rod 22-2 stroke of 1000mm, the pin diameters at the top and tail of the hydraulic cylinder 22 are 50mm, and the oil port size is M22×1.5.

[0079] As a specific embodiment, the oil pump 8 is an adjustable gear pump with an adjustment range of 80-100 L / min. The rated pressure of the hydraulic system is P max It is 16MPa.

[0080] As a specific embodiment, a third pressure sensor is provided on the steel wire rope 23. The steel wire rope 23 with the tension sensor is located on the gantry of the test bench, and the pressure value on the steel wire rope is remotely displayed in real time through the control system.

[0081] As a specific embodiment, the first oil tank 1 is also provided with an oil gauge, which displays the oil level in the tank through a remote control system and can be added and unloaded manually.

[0082] This invention proposes a dynamic loading hydraulic device for a hydraulic cylinder 22 anti-lifting test bench. This device can be used for tensile testing of new capstans. It can detect the load tension and speed of the hydraulic cylinder 22 under dynamic load conditions, overcoming the influence of the hydraulic system on tensile test results. It also adjusts the pressure of the pilot relief valve and the flow direction of the electro-hydraulic reversing valve to optimize system performance and avoid oscillation. Through a remote control system, the system can precisely control load force and displacement, further improving test accuracy. It achieves both anti-lifting and coordinated free-fall functions.

[0083] The technical features of the above embodiments can be combined arbitrarily. To make the description concise, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0084] This document uses specific examples to illustrate the principles and implementation methods of the present invention. The above examples are only intended to help understand the method and core concept of the present invention. At the same time, those skilled in the art will find that the specific implementation methods and application scopes may vary based on the concept of the present invention. In summary, the contents of this specification should not be construed as limiting the present invention.

Claims

1. A dynamic loading hydraulic device for a hydraulic cylinder against a lifting test bench, characterized in that: The device includes a hydraulic oil suction device, a normally open electromagnetic overflow valve, a first oil tank, a first hydraulic oil return path, an electro-hydraulic reversing valve, a hydraulic cylinder, a first oil path, a second oil path, a third oil path, a second hydraulic oil return path and a steel rope; One end of the hydraulic oil suction device is respectively connected to the first port of the electro-hydraulic reversing valve and the input port of the normally open electromagnetic relief valve; the output port of the normally open electromagnetic relief valve is respectively connected to one end of the first hydraulic oil return path and the second port of the electro-hydraulic reversing valve; the other end of the hydraulic oil suction device and the other end of the first hydraulic oil return path are both connected to the first oil tank; The third port of the electro-hydraulic reversing valve is connected to one end of the first oil circuit; the other end of the first oil circuit is connected to the rodless chamber of the hydraulic cylinder; The fourth port of the electro-hydraulic reversing valve is in communication with one end of the second oil circuit; the other end of the second oil circuit is in communication with one end of the third oil circuit and one end of the second hydraulic oil return passage, respectively; the other end of the third oil circuit is in communication with the rod chamber of the hydraulic cylinder; the other end of the second hydraulic oil return passage is in communication with the second oil tank; The hydraulic rod of the hydraulic cylinder is connected to the steel wire rope; the steel wire rope is connected to the capstan to be tested; The working process of the hydraulic cylinder resisting the dynamic load of the capstan to be tested specifically includes: The hydraulic oil suction device sucks hydraulic oil from the first oil tank and delivers the hydraulic oil to the normally open electromagnetic relief valve; the normally open electromagnetic relief valve returns the unloaded hydraulic oil in the hydraulic oil to the first oil tank through the hydraulic oil first return passage; The winch to be tested drives the hydraulic rod of the hydraulic cylinder to move through the wire rope, so that the target hydraulic oil in the rod chamber enters the second return path of the hydraulic oil through the third oil circuit; the normally open electromagnetic overflow valve transports the opposing hydraulic oil in the hydraulic oil to the second oil circuit through the electro-hydraulic reversing valve; the second oil circuit transports the opposing hydraulic oil to the second return path of the hydraulic oil; the second return path of the hydraulic oil transports the opposing hydraulic oil and the target hydraulic oil to the second oil tank; wherein, the pressure value set in the second return path of the hydraulic oil is the current load value of the hydraulic cylinder.

2. The dynamic loading hydraulic device of the hydraulic cylinder anti-lifting test bench according to claim 1 is characterized in that: The normally open electromagnetic relief valve includes a first pilot relief valve and a two-position two-way electromagnetic reversing valve; The input end of the first pilot relief valve is communicated with one end of the hydraulic oil suction device and the first port of the electro-hydraulic reversing valve respectively; the output end of the first pilot relief valve is communicated with one end of the first hydraulic oil return passage and the second port of the electro-hydraulic reversing valve respectively; the control oil outlet of the first pilot relief valve is communicated with the first port of the two-position two-way solenoid reversing valve; the second port of the two-position two-way solenoid reversing valve is communicated with one end of the first hydraulic oil return passage.

3. The dynamic loading hydraulic device of the hydraulic cylinder anti-lifting test bench according to claim 1 is characterized in that: The electro-hydraulic directional control valve includes a hydraulic directional control valve and a three-position four-way electromagnetic directional control valve; The first port of the hydraulic reversing valve is connected to one end of the first oil circuit; the second port of the hydraulic reversing valve is connected to one end of the second oil circuit; the third port of the hydraulic reversing valve is connected to the third port of the three-position four-way solenoid reversing valve; the fourth port of the hydraulic reversing valve is connected to the fourth port of the three-position four-way solenoid reversing valve; the first port of the three-position four-way solenoid reversing valve is connected to the second pressure oil inlet of the hydraulic reversing valve; the second port of the three-position four-way solenoid reversing valve is connected to the first pressure oil inlet of the hydraulic reversing valve; the third port of the three-position four-way solenoid reversing valve is connected to the input port of the normally open electromagnetic overflow valve; the fourth port of the three-position four-way solenoid reversing valve is connected to the output port of the normally open electromagnetic overflow valve.

4. The dynamic loading hydraulic device of the hydraulic cylinder anti-lifting test bench according to claim 1 is characterized in that: The second hydraulic oil return passage includes a second pilot relief valve and a second pressure sensor; One end of the second pilot relief valve is connected to the other end of the second oil circuit; the other end of the second pilot relief valve is connected to the second oil tank; The second pressure sensor is connected to one end of the second pilot relief valve; the second pressure sensor is used to detect the pressure of the hydraulic oil flowing into the second pilot relief valve; the hydraulic oil flowing into the second pilot relief valve includes the target hydraulic oil and the opposing hydraulic oil.

5. The dynamic loading hydraulic device of the hydraulic cylinder anti-lifting test bench according to claim 1 is characterized in that: The second oil circuit includes a second one-way valve; One end of the second one-way valve is communicated with the fourth port of the electro-hydraulic reversing valve; the other end of the second one-way valve is communicated with one end of the third oil circuit.

6. The dynamic loading hydraulic device of the hydraulic cylinder anti-lifting test bench according to claim 1 is characterized in that: The first oil circuit includes a throttle valve and a first stop ball valve; One end of the throttle valve is communicated with the third port of the electro-hydraulic reversing valve; the other end of the throttle valve is communicated with one end of the first stop ball valve; the other end of the first stop ball valve is communicated with the rodless chamber of the hydraulic cylinder.

7. The dynamic loading hydraulic device of the hydraulic cylinder anti-lifting test bench according to claim 1 is characterized in that: The third oil circuit includes a second stop ball valve; One end of the second cut-off ball valve is communicated with the other end of the second oil circuit; the other end of the second cut-off ball valve is communicated with the rod chamber of the hydraulic cylinder.

8. The dynamic loading hydraulic device of the hydraulic cylinder anti-lifting test bench according to claim 1 is characterized in that: The first hydraulic oil return path includes a cooler, a fan and a flow sensor; One end of the cooler is connected to the output port of the normally open electromagnetic overflow valve; The fan is used to accelerate the cooling speed of the cooler; The other end of the cooler is communicated with one end of the flow sensor; The other end of the flow sensor is communicated with the first oil tank.

9. The dynamic loading hydraulic device of the hydraulic cylinder anti-lifting test bench according to claim 1, characterized in that: The hydraulic oil suction device includes a filter, an oil pump motor, an oil pump, a first one-way valve and a first pressure sensor; One end of the filter is connected to the first oil tank; the other end of the filter is connected to one end of the oil pump; the other end of the oil pump is connected to one end of the first one-way valve; the other end of the first one-way valve is connected to the input port of the normally open electromagnetic overflow valve; The first pressure sensor is connected to the input port of the normally open electromagnetic relief valve; The oil pump motor is connected to the oil pump; the oil pump motor is used to drive the oil pump to work.

10. The dynamic loading hydraulic device of the hydraulic cylinder anti-lifting test bench according to claim 1, characterized in that: The device also includes a temperature sensor; The temperature sensor is used to detect the temperature of the hydraulic oil in the first oil tank.

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