Dynamic loading hydraulic device of hydraulic cylinder anti-hoisting test bed

Abstract

The invention discloses a dynamic loading hydraulic device of a hydraulic cylinder anti-hoisting test bed, and relates to the field of hydraulic loading of winching machine tension test. According to the device, one end of a hydraulic oil suction device is communicated with a first port of an electro-hydraulic directional control valve and an input port of a normally-open electromagnetic relief valve, and the other end of the hydraulic oil suction device and the other end of a first hydraulic oil return passage are both communicated with a first oil tank; an output port of the normally open electromagnetic relief valve is communicated with one end of a first hydraulic oil return passage and a second port of the electro-hydraulic directional control valve respectively; one end of the first oil way is communicated with a third port of the electro-hydraulic reversing valve, and the other end of the first oil way is communicated with a rodless cavity of the hydraulic cylinder; one end of the second oil way is communicated with a fourth port of the electro-hydraulic reversing valve, and the other end of the second oil way is respectively communicated with one end of the third oil way and one end of the second hydraulic oil return passage; the other end of the third oil way is communicated with a rod cavity of the hydraulic cylinder; the other end of the hydraulic oil second return passage is communicated with the second oil tank. The precision of the pressure test result of the winching machine is improved.

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 docks, especially in the assembly of pole towers and hoisting and traction. At present, when capstans are developed and shipped, they lack a dynamic load condition and a device that can detect their tension and wire rope speed in a timely manner. There are few hydraulic systems for dynamic loading resistance in the prior art, and there is a lack of how to use hydraulic cylinders to load the lifting test bench, and there is a lack of hydraulic systems that overcome the tension test of the hydraulic system and ensure the stability of loading. The dynamic loading hydraulic system will cause a series of complex effects in the capstan test, 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 of a hydraulic cylinder against a lifting test bench, which can improve the accuracy of a pressure test result 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 against a lifting test bench, the device 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 communicated with one end of the first oil circuit; the other end of the first oil circuit is communicated with 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 return passage of the hydraulic oil 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 return passage of the hydraulic oil 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 against the lifting dynamic load of the capstan to be tested 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 overflow valve; the normally open electromagnetic overflow 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 second return passage of the hydraulic oil through the above-mentioned third oil passage; the above-mentioned normally open electromagnetic overflow valve conveys the antagonistic hydraulic oil in the above-mentioned hydraulic oil to the above-mentioned second oil passage through the above-mentioned electro-hydraulic reversing valve; the above-mentioned second oil passage conveys the above-mentioned antagonistic hydraulic oil to the above-mentioned second return passage of the hydraulic oil; the above-mentioned second return passage of the hydraulic oil conveys the above-mentioned antagonistic hydraulic oil and the above-mentioned target hydraulic oil to the above-mentioned second oil tank; wherein, the pressure value set for the above-mentioned second return passage of the hydraulic oil is the current load value of the above-mentioned hydraulic cylinder.

[0013] Optionally, the normally open electromagnetic relief valve comprises 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 connected 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 connected 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 connected 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 connected with one end of the above-mentioned hydraulic oil first return passage.

[0015] Optionally, the electro-hydraulic reversing valve comprises a hydraulic reversing valve and a three-position four-way electromagnetic reversing valve;

[0016] 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 electromagnetic reversing valve is connected to the output port of the normally open electromagnetic overflow valve.

[0017] Optionally, the second hydraulic oil return passage comprises 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 counter 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 comprises 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 comprises 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 first hydraulic oil 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 overflow valve;

[0028] The fan is used to speed up 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 comprises 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 overflow 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 comprises 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-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 realize 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 passage of the hydraulic oil. With the change of the tension of the wire rope, the process of anti-hydraulic system can be realized by adjusting the pressure of the second return passage 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 the 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 its tension and wire rope speed can be detected under dynamic load conditions, overcoming the influence of the hydraulic system on the tension test results, and realizing the functions of anti-lifting and coordinated free-falling. 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 drawings required for use in the embodiments will be briefly introduced below. 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 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 A 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 A schematic diagram of an application scenario of a dynamic loading hydraulic device of 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 reversing valve; 11: First pilot relief valve; 12: First pressure sensor; 13: Three-position four-way solenoid reversing 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 be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. 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 creative work 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, so as to improve the accuracy of the pressure test result 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 cylinder 22 resists the dynamic loading hydraulic device of the lifting test bench, comprising: a hydraulic oil suction device, a normally open electromagnetic overflow valve, a first oil tank 1, a first return path of hydraulic oil, an electro-hydraulic reversing valve, a hydraulic cylinder 22, a first oil circuit, a second oil circuit, a third oil circuit, a second return path of hydraulic oil and a steel wire rope 23. The hydraulic oil suction device, the normally open electromagnetic overflow valve, the first oil tank 1, the first return path of hydraulic oil, the electro-hydraulic reversing valve, the hydraulic cylinder 22, the first oil circuit, the second oil circuit, the third oil circuit, the second return path of hydraulic oil and the steel wire rope 23 are all connected through a pipeline 24.

[0051] 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 return passage of hydraulic oil 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 return passage of hydraulic oil are both connected to the first oil tank 1. The hydraulic oil suction device is used to suck hydraulic oil from the first oil tank and transport 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 implementation, the normally open electromagnetic relief valve includes a first pilot relief valve 11 and a two-position two-way electromagnetic reversing valve 10. When not powered, 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 the 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 the hydraulic oil.

[0058] As a specific implementation, the electro-hydraulic reversing valve includes a hydraulic reversing valve 14 and a three-position four-way electromagnetic reversing valve 13. Among them, the three-position four-way electromagnetic reversing valve 13 includes a left electromagnet 13-1 and a right electromagnet 13-2. Corresponding to the different power-on states of the two electromagnets, the three-position four-way electromagnetic reversing valve 13 has three different working positions: left, middle, and right. When the left electromagnet 13-1 and the right electromagnet 13-2 are not powered, the three-position four-way electromagnetic reversing valve 13 is in a middle 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 electromagnetic reversing valve 13; the fourth port of the hydraulic reversing valve 14 is connected to the fourth port of the three-position four-way electromagnetic reversing valve 13; the first port of the three-position four-way electromagnetic 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 electromagnetic 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 electromagnetic 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 electromagnetic reversing valve 13 is connected to the output port of the normally open electromagnetic overflow valve.

[0060] As a specific implementation, 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 the 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 counter hydraulic oil.

[0063] As a specific implementation, the second oil circuit includes a second one-way valve 18. One end of the second one-way valve 18 is communicated with the fourth port of the electro-hydraulic reversing valve; the other end of the second one-way valve 18 is communicated with 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 implementation, 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 passage 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 implementation, 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 implementation, 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 lifting 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 passage; 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 sucks hydraulic oil from the first oil tank 1. The hydraulic oil first passes through the filter 2 from the pipeline 1 24-1 and then is sucked into the oil pump 8 from the pipeline 2 24-2. Then, the hydraulic oil passes through the first check valve 9 from the pipeline 3 24-3, the pipeline 4 24-4, the pipeline 6 24-6 directly pass through the first pilot relief valve 11, and then through the pipeline 7 24-7, the pipeline 10 24-10, the cooler 5, the pipeline 11 24-11, the flow sensor 4, and the pipeline 12 24-12 to flow back to the first oil tank 1, thereby realizing low-pressure unloading of the system.

[0073] The capstan to be tested drives the hydraulic rod 22-2 of the hydraulic cylinder 22 to move through the steel wire rope 23, so that the target hydraulic oil in the rod chamber 22-1 enters the second return path of the hydraulic oil through the third oil path; the normally open electromagnetic overflow valve delivers the opposing hydraulic oil in the hydraulic oil to the second oil path through the electro-hydraulic reversing valve; the second oil path delivers the opposing hydraulic oil to the second return path of the hydraulic oil; the second return path of the hydraulic oil delivers the opposing hydraulic oil and the target hydraulic oil to the second oil tank 15; wherein the pressure value set in the second return path of the hydraulic oil 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] When the hydraulic cylinder 22 is lifting the capstan to be tested, oil is sucked in from pipeline 13 24-13 through the T port of the Y-type reversing valve, and passes through pipeline 14 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 pipeline 19 24-19 and pipeline 17 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 antagonistic hydraulic system. At this time, the normally open electromagnetic overflow valve in the system is in the open state because it is not powered on, so as to realize 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 powered on and are in the middle working state.

[0077] When the hydraulic loading device is in the free-falling condition 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 powered on 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 position 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 check 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, flow sensor 4, 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 a 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, a pin diameter of 50mm at the top and tail of the hydraulic cylinder 22, and an oil port size of M22×1.5.

[0079] As a specific implementation, 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 P max It is 16MPa.

[0080] As a specific implementation, a third pressure sensor is provided on the steel wire rope 23. The steel wire rope 23 with the tension sensor is 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 implementation, the first oil tank 1 is also provided with an oil gauge, which displays the oil level in the oil tank through a remote control system, and can be added and unloaded manually.

[0082] The present invention proposes a dynamic loading hydraulic device for a hydraulic cylinder 22 against lifting test bench, which can be applied to the tension test of a new type of capstan grinder. The load tension and speed of the hydraulic cylinder 22 can be detected under dynamic load conditions, overcoming the influence of the hydraulic system on the tension test results. The pressure of the pilot relief valve and the flow direction of the electro-hydraulic reversing valve can also be adjusted to optimize system performance and avoid oscillation. Through the remote control system, the system can accurately control the load force and displacement, further improving the test accuracy. The functions of against lifting and coordinated free descent are realized.

[0083] The technical features of the above embodiments may 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] The principles and implementation methods of the present invention are described in this article using specific examples. The description of the above embodiments is only used to help understand the method and core idea of ​​the present invention. At the same time, for those skilled in the art, according to the idea of ​​the present invention, there will be changes in the specific implementation methods and application scope. In summary, the content of this specification should not be understood 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 comprises a hydraulic oil suction device, a normally open electromagnetic overflow valve, a first oil tank, a first hydraulic oil return passage, an electro-hydraulic reversing valve, a hydraulic cylinder, a first oil circuit, a second oil circuit, a third oil circuit, a second hydraulic oil return passage and a steel wire 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 overflow valve; the output port of the normally open electromagnetic overflow valve is respectively connected to one end of the hydraulic oil first 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 hydraulic oil first return passage are both connected to the first oil tank; 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 of the hydraulic cylinder; The fourth port of the electro-hydraulic reversing valve is communicated with one end of the second oil circuit; the other end of the second oil circuit is respectively communicated with one end of the third oil circuit and one end of the second return passage of the hydraulic oil; the other end of the third oil circuit is communicated with the rod chamber of the hydraulic cylinder; the other end of the second return passage of the hydraulic oil is communicated 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 against the lifting 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 overflow valve; the normally open electromagnetic overflow valve returns the unloaded hydraulic oil in the hydraulic oil to the first oil tank through the hydraulic oil first return passage; The capstan 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 antagonistic hydraulic oil in the hydraulic oil to the second oil circuit through the electro-hydraulic reversing valve; the second oil circuit transports the antagonistic hydraulic oil to the second return path of the hydraulic oil; the second return path of the hydraulic oil transports the antagonistic hydraulic oil and the target hydraulic oil to the second oil tank; wherein, the pressure value set for 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 comprises 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 return passage of the hydraulic oil 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 return passage of the hydraulic oil.

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 reversing valve includes a hydraulic reversing valve and a three-position four-way electromagnetic reversing 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 electromagnetic 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 counter 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 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.

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 in communication with 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 connected to 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 is 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 in communication with an 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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