Comprehensive test system and method for circular seam throttling hydraulic buffer device

Abstract

The invention relates to the technical field of hydraulic cylinder throttling and buffering performance testing, in particular to a comprehensive testing system and method for a circular seam throttling and hydraulic buffering device. The buffer is arranged, the detachable test cylinder and the throttling small hole are arranged to carry out a rapid disassembly and assembly combined test, and buffer performance test analysis of hydraulic cylinders of different structure sizes and data analysis of fluid impact force in a buffer cavity are achieved; a test platform is provided for prototype design and optimization of the circular seam throttling hydraulic buffer device, the feasibility of a new product is ensured, and the overall research and development efficiency is effectively improved; and the circular seam throttling buffer initial section is arranged to be a conical surface with a certain angle, so that the impact force generated by fluid in the buffer cavity when the hydraulic cylinder enters the buffer stage is effectively reduced.

Description

Technical Field

[0001] The invention relates to the technical field of hydraulic cylinder throttling buffer performance detection, in particular to a comprehensive test system and method for an annular gap throttling hydraulic buffer device. Background Art

[0002] With the continuous development of my country's industrial technology, hydraulic cylinders, as a hydraulic actuator that performs linear reciprocating motion, have the ability to convert hydraulic energy into mechanical energy and are widely used in the hydraulic systems of petrochemical machinery, engineering machinery, and aviation machinery. During the use of hydraulic cylinders, there are often problems such as easy collision at the end of the stroke and unclear friction of the sealing rubber ring, which leads to abnormal wear of the hydraulic cylinder parts or seal failure, and even abnormal collision and vibration of the entire mechanism, affecting the reliability of the product. Therefore, the end buffer performance of the hydraulic cylinder has received much attention during the development process.

[0003] At present, the commonly used buffer devices are mainly divided into the following categories: rubber buffer, friction buffer, spring buffer, pneumatic buffer, hydraulic buffer. Compared with other buffer devices, the annular gap throttling hydraulic buffer has the advantages of stable performance, high buffering efficiency, and easy adjustment. However, the corresponding buffer performance test system is very scarce, especially the test system that can be used to test key technologies such as sealing rubber friction and buffer chamber fluid impact force is small, and the test object is single, the versatility is poor, the equipment cost is too high, and the data acquisition and processing system is not perfect.

[0004] The proposed comprehensive test system and method for the annular gap throttling hydraulic buffer device must meet the following requirements:

[0005] 1. When the annular gap throttling hydraulic buffer device enters the buffer stage, the impact force generated by the fluid itself should be small;

[0006] 2. The comprehensive test system for the buffer device should be able to perform buffer performance tests on hydraulic cylinders of different structural sizes;

[0007] 3. The comprehensive test system of the buffer device should be able to simulate the load condition of the hydraulic cylinder realistically and detect the fluid impact force of the hydraulic cylinder buffer chamber and the friction force of the sealing rubber;

[0008] 4. The comprehensive test system for buffer devices can provide full real-time monitoring and feedback on the test process, and quickly and accurately collect and analyze the required data. Summary of the invention

[0009] In view of the problems of the existing test system, such as single test object, poor versatility, excessively high equipment cost and imperfect data acquisition and processing system, the present invention proposes a comprehensive test system and method for an annular gap throttling hydraulic buffer device; by setting a buffer, a detachable test cylinder and a throttling hole are set to carry out a quick disassembly and assembly combination test, thereby realizing the test analysis of the buffer performance of hydraulic cylinders of different structural sizes and the data analysis of the impact force of the fluid in the buffer cavity; providing a test platform for the prototype design and optimization of the annular gap throttling hydraulic buffer device, ensuring the feasibility of new products and effectively improving the overall research and development efficiency.

[0010] The specific implementation contents of the present invention are as follows:

[0011] A comprehensive test system for annular gap throttling hydraulic buffer device, comprising a power source module, a load force adjustment module, a buffer performance test module, and an electrical signal control module;

[0012] The buffer performance test module includes a force sensor, a loading cylinder, a detachable test cylinder, and a detachable throttling orifice;

[0013] The power source module is connected to the buffer performance test module through a hydraulic pipeline;

[0014] The electrical signal control module includes a control circuit and a controller;

[0015] The load force adjustment module is connected to the buffer performance test module through a hydraulic pipeline;

[0016] The electric signal control module is connected with the power source module, the load force adjustment module and the buffer performance test module;

[0017] The force sensor is arranged between the loading cylinder and the test cylinder;

[0018] The throttling hole is arranged between the test cylinder and the power source module.

[0019] In order to better realize the present invention, further, the test cylinder includes an oil inlet chamber, an outer cylinder, a test cylinder piston rod, a buffer chamber, a buffer cone surface, a buffer gap, and an oil return chamber;

[0020] The oil inlet chamber, buffer chamber and oil return chamber are all arranged in the outer cylinder;

[0021] The oil return chamber is connected to the power source module;

[0022] A buffer cone is provided at the buffer starting section of the buffer cavity, and the buffer cavity is communicated with the oil return cavity through a buffer gap.

[0023] In order to better implement the present invention, further, the length of the buffer cone surface is half of the buffer course of the buffer cavity.

[0024] In order to better implement the present invention, further, the buffer gap is an annular gap throttling.

[0025] In order to better implement the present invention, further, the buffer performance test module also includes a second three-position four-way electromagnetic reversing valve, a displacement sensor, a second pressure sensor, and a third pressure sensor;

[0026] The three-position four-way electromagnetic reversing valve is connected to the power source module, the loading cylinder, and the load force adjustment module;

[0027] One end of the displacement sensor is connected to the force sensor, and the other end is connected to the controller;

[0028] One end of the second pressure sensor is connected to the controller, and the other end is connected to the test cylinder;

[0029] One end of the third pressure sensor is overlapped between the test cylinder and the throttling hole, and the other end is connected to the controller.

[0030] In order to better realize the present invention, further, the power source module includes an oil level sensor, a filter, an oil tank, a first electric plunger pump, a second electric plunger pump, a first check valve, a proportional relief valve, a first two-position two-way electromagnetic reversing valve, a second check valve and a third check valve;

[0031] The oil level sensor is arranged on the oil tank;

[0032] The first electric plunger pump is connected to the three-position four-way electromagnetic reversing valve through a third one-way valve;

[0033] The second electric plunger pump is connected to the throttling orifice through a second one-way valve;

[0034] One end of the filter is connected to the oil tank, and the other end is connected to the first electric plunger pump and the second electric plunger pump;

[0035] One end of the proportional relief valve is connected to the controller, and the other end is overlapped between the second one-way valve and the throttling orifice;

[0036] The first two-position two-way electromagnetic reversing valve is connected with a controller, a first one-way valve, a proportional relief valve, a second one-way valve, and a throttling orifice.

[0037] In order to better realize the present invention, further, the load force adjustment module includes a first direct-acting relief valve, a second direct-acting relief valve, a first three-position four-way electromagnetic reversing valve, a third direct-acting relief valve, a fourth one-way valve, a second two-position two-way electromagnetic reversing valve and a first pressure sensor;

[0038] The first direct-acting relief valve and the second direct-acting relief valve are connected to the oil tank and the first three-position four-way electromagnetic reversing valve;

[0039] The first three-position four-way electromagnetic reversing valve is connected to the controller via a control line;

[0040] The third direct-acting relief valve is connected to the first three-position four-way electromagnetic reversing valve, the controller, the third one-way valve, and the second three-position four-way electromagnetic reversing valve;

[0041] The second two-position two-way electromagnetic reversing valve is connected to the fourth one-way valve, the second three-position four-way electromagnetic reversing valve, the controller, and the loading cylinder;

[0042] One end of the first pressure sensor is overlapped with the second two-position two-way electromagnetic reversing valve and connected to the loading cylinder, and the other end is connected to the controller through a control line.

[0043] In order to better implement the present invention, further, the electrical signal control module also includes a human-computer interaction interface;

[0044] The human-computer interaction interface is used to display system pressure data, system displacement data, and system thrust data in real time.

[0045] Based on the above-mentioned annular gap throttling hydraulic buffer device comprehensive test system, in order to better realize the present invention, further, a annular gap throttling hydraulic buffer device comprehensive test method is proposed, which is based on the above-mentioned annular gap throttling hydraulic buffer device comprehensive test system and specifically includes the following steps:

[0046] Step S1: Connect the force sensor to the test cylinder and the loading cylinder through threads, and connect the hydraulic pipeline of the system, check whether the control line is connected, debug the electrical signal control module, and set necessary parameters;

[0047] Step S2: by controlling the first electric piston pump to operate, the second three-position four-way electromagnetic reversing valve to be powered on, and the loading cylinder to extend, the force sensor detection data is obtained, and the piston positions of the test cylinder and the loading cylinder are adjusted to the initial stage at the right end, so as to complete the piston seal friction test; the force sensor detection data is the test cylinder piston seal friction;

[0048] Step S3: by controlling the operation of the first electric piston pump and the power-on of the first three-position four-way electromagnetic reversing valve, analyzing the piston rod displacement time function fed back by the displacement sensor, analyzing the buffering performance, and secondly analyzing the pressure time function fed back by the pressure sensor, corresponding to whether there is a sharp increase in pressure when the test cylinder enters the buffering moment, converting the pressure peak into the impact force of the fluid in the buffer chamber, and completing the buffering performance test;

[0049] Step S4: Replace the test cylinder and throttling orifice with different structural sizes and repeat steps S1 to S3 to complete the performance analysis test of the remaining buffer structures. According to the test result report, comprehensively evaluate the end buffer performance of the hydraulic cylinder when the annular gap and the orifice are combined for throttling.

[0050] In order to better implement the present invention, further, the step S2 specifically includes the following steps:

[0051] Step S21: Control the first electric piston pump to operate, the second three-position four-way electromagnetic reversing valve to be powered on, and the loading cylinder to extend;

[0052] Step S22: When YA4 of the second three-position four-way solenoid reversing valve is powered on, the first two-position two-way solenoid reversing valve is powered on, the oil return chamber of the test cylinder is directly connected to the oil tank, the test cylinder runs without load, and the force sensor detection data obtained is used as the friction force of the test cylinder piston seal;

[0053] Step S23: Control YA3 of the second three-position four-way electromagnetic reversing valve to power on, adjust the piston positions of the test cylinder and the loading cylinder to the right end initial stage, and complete the piston seal friction test.

[0054] In order to better implement the present invention, further, the step S3 specifically includes the following steps:

[0055] Step S31: Control the first electric plunger pump to operate, power on YA4 of the first three-position four-way solenoid reversing valve, adjust the pressure of the loading cylinder by the third direct-acting relief valve, move the piston rod of the loading cylinder to the left, push the test cylinder to move to the left, and adjust the load of the test cylinder by the proportional relief valve;

[0056] Step S32: providing three pressure supplies to the loading cylinder through the first direct-acting relief valve, the second direct-acting relief valve and the third direct-acting relief valve according to the actual unloading pressure of the proportional relief valve;

[0057] Step S33: When the test cylinder reaches the end of the stroke, observe whether the piston rod speed of the test cylinder is significantly slowed down, and whether the device has vibration or impact;

[0058] Step S34: Analyze the time function of the piston rod displacement of the test cylinder fed back by the displacement sensor, analyze the buffering performance based on the time function, and analyze the pressure-time function fed back by the second pressure sensor, and determine whether there is a sharp increase in pressure when the test cylinder enters the buffering state based on the pressure-time function, and convert the pressure peak into the impact force of the fluid in the buffer chamber.

[0059] In order to better implement the present invention, further, the step S4 specifically includes the following steps:

[0060] Step S41: replacing annular gap throttling test cylinders of different sizes to execute steps S1 to S3, and comprehensively evaluating the end buffer performance of the hydraulic cylinder when only the annular gap throttling is performed;

[0061] Step S42: Replace the test cylinder with a hydraulic cylinder without buffering performance, execute steps S1 to S3, and replace the throttling orifices with different structural sizes, and comprehensively evaluate the end buffering performance of the hydraulic cylinder when only the orifice is throttled;

[0062] Step S43: Replace the annular gap throttling test cylinder and the throttling orifice with different structural sizes to execute steps S1 to S3, and comprehensively evaluate the end buffer performance of the hydraulic cylinder when the annular gap and the orifice are combined for throttling.

[0063] The present invention has the following beneficial effects:

[0064] (1) The present invention realizes the test analysis of the buffering performance of hydraulic cylinders of different structural sizes and the data analysis of the impact force of the fluid in the buffer chamber by arranging a detachable test cylinder and a throttling hole for rapid disassembly and assembly test, thereby providing a test platform for the prototype design and optimization of the annular gap throttling hydraulic buffer device, ensuring the feasibility of new products and effectively improving the overall research and development efficiency.

[0065] (2) The present invention effectively reduces the impact force generated by the fluid in the buffer chamber when the hydraulic cylinder enters the buffer stage by providing a conical surface with a certain angle at the starting section of the annular gap throttling buffer.

[0066] (3) The loading cylinder provided in the present invention can provide four load forces, thereby simulating the full working conditions of the buffer hydraulic cylinder and effectively testing the friction force of the rubber sealing ring of the hydraulic cylinder.

[0067] (4) The sensors and controllers provided in the present invention realize real-time monitoring of the test process and effectively transform the microscopic buffering performance and the impact pressure of the fluid inside the buffer cavity into macroscopic test data. BRIEF DESCRIPTION OF THE DRAWINGS

[0068] Figure 1 A schematic structural diagram of a comprehensive test system for annular gap throttling hydraulic buffer device provided by the present invention.

[0069] Figure 2 This is a structural principle diagram of the annular gap throttling hydraulic buffer device provided by the present invention.

[0070] Figure 3 This is a schematic diagram of the data acquisition control principle provided by the present invention.

[0071] Figure 4 The present invention provides a flow chart of a buffering performance test method.

[0072] Among them, 1. power source module, 2. load force adjustment module, 3. buffer performance test module, 4. electrical signal control module, 101. oil level sensor, 102. filter, 103. oil tank, 104. first electric piston pump, 105. second electric piston pump, 106. first check valve, 107. proportional relief valve, 108. first two-position two-way solenoid reversing valve, 109. second check valve, 110. third check valve, 201. first direct-acting relief valve, 202. second direct-acting relief valve, 203. first three-position four-way solenoid reversing valve, 204. third direct-acting relief valve, 205. fourth check valve, 206. 6. Second two-position two-way solenoid reversing valve, 207. First pressure sensor, 301. Second three-position four-way solenoid reversing valve, 302. Loading cylinder, 303. Force sensor, 304. Displacement sensor, 305. Test cylinder, 306. Second pressure sensor, 307. Third pressure sensor, 308. Throttling hole, 401. Human-machine interface, 402. Control circuit, 403. Controller, 3051. Oil inlet chamber, 3052. Outer cylinder, 3053. Piston rod, 3054. Buffer chamber, 3055. Buffer stroke, 3056. Buffer cone, 3057. Buffer gap, 3058. Oil return chamber. DETAILED DESCRIPTION

[0073] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. It should be understood that the described embodiments are only part of the embodiments of the present invention, not all of the embodiments, and therefore should not be regarded as limiting the scope of protection. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technical personnel in this field without making creative work are within the scope of protection of the present invention.

[0074] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "disposed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be an indirect connection through an intermediate medium, or it can be the internal communication of two elements. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0075] Embodiment 1:

[0076] This embodiment provides a comprehensive test system for annular gap throttling hydraulic buffer device, such as Figure 1 As shown, it includes a power source module 1, a load force adjustment module 2, a buffer performance test module 3, and an electrical signal control module 4;

[0077] The buffer performance test module 3 includes a force sensor 303, a loading cylinder 302, a detachable test cylinder 305, and a detachable throttling orifice 308;

[0078] The power source module 1 is connected to the buffer performance test module 3 through a hydraulic pipeline;

[0079] The electrical signal control module 4 includes a control circuit 402 and a controller 403;

[0080] The load force adjustment module 2 is connected to the buffer performance testing module 3 through a hydraulic pipeline;

[0081] The electric signal control module 4 is connected to the power source module 1, the load force adjustment module 2 and the buffer performance test module 3;

[0082] The force sensor 303 is disposed between the loading cylinder 302 and the test cylinder 305;

[0083] The throttling hole 308 is arranged between the test cylinder 305 and the power source module 1 .

[0084] Working principle: This embodiment realizes the test analysis of the buffering performance of hydraulic cylinders of different structural sizes and the data analysis of the fluid impact force in the buffer chamber by setting a detachable test cylinder and a throttling hole for rapid disassembly and assembly test; it provides a test platform for the prototype design and optimization of the annular seam throttling hydraulic buffer device, ensures the feasibility of new products, and effectively improves the overall R&D efficiency.

[0085] Embodiment 2:

[0086] This embodiment is based on the above embodiment 1. Figure 1 , Figure 2 As shown, the specific structure of the buffer performance test module 3 is described.

[0087] The buffer performance test module 3 also includes a second three-position four-way electromagnetic reversing valve 301, a displacement sensor 304, a second pressure sensor 306, and a third pressure sensor 307;

[0088] The three-position four-way electromagnetic reversing valve 301 is connected to the power source module 1, the loading cylinder 302, and the load force adjustment module 2;

[0089] One end of the displacement sensor 304 is connected to the force sensor 303, and the other end is connected to the controller 403;

[0090] One end of the second pressure sensor 306 is connected to the controller 403, and the other end is connected to the test cylinder 305;

[0091] One end of the third pressure sensor 307 is overlapped between the test cylinder 305 and the throttling hole 308 , and the other end is connected to the controller 403 .

[0092] The test cylinder 305 includes an oil inlet chamber 3051, an outer cylinder 3052, a test cylinder piston rod 3053, a buffer chamber 3054, a buffer cone 3056, a buffer gap 3057, and an oil return chamber 3058;

[0093] The oil inlet chamber 3051, the buffer chamber 3054, and the oil return chamber 3058 are all arranged in the outer cylinder 3052;

[0094] The oil return chamber 3058 is connected to the power source module 1;

[0095] The buffer starting section of the buffer cavity 3054 is provided with a buffer cone surface 3056 , and the buffer cavity 3054 is connected with the oil return cavity 3058 through a buffer gap 3057 .

[0096] The length of the buffer cone 3056 provided in this embodiment is half of the buffer process 3055 of the buffer cavity 3054 .

[0097] The buffer gap 3057 provided in this embodiment is annular gap throttling.

[0098] Working principle: The buffer performance test module 3 provided in this embodiment includes a second three-position four-way electromagnetic reversing valve 301, a loading cylinder 302, a force sensor 303, a displacement sensor 304, a test cylinder 305, a second pressure sensor 306, a third pressure sensor 307 and a throttling hole 308.

[0099] The force sensor 303 is connected to the piston rod of the loading cylinder 302 and the piston rod of the test cylinder 305 respectively through threads.

[0100] The test cylinder 305 includes an oil inlet chamber 3051, an outer tube 3052, a piston rod 3053, a buffer chamber 3054, a buffer stroke 3055, a buffer cone 3056, a buffer gap 3057, and an oil return chamber 3058. The length of the buffer cone 3056 is half of the buffer stroke 3055. The provision of the buffer cone 3056 can significantly reduce the impact force generated by the fluid itself when the hydraulic cylinder enters the buffer stage.

[0101] The buffer gap 3057 of the test cylinder 305 is an annular gap throttling, and the throttling hole 308 is a small hole throttling. The test cylinder 305 and the throttling hole 308 can be quickly disassembled and assembled for combined testing.

[0102] The loading cylinder 302 adopts three-stage pressure regulation. The first three-position four-way solenoid reversing valve 203 is not energized. The system pressure of the loading cylinder 302 is regulated by the three-position direct-acting overflow valve 204. The first three-position four-way solenoid reversing valve 203YA1 is energized. The system pressure of the loading cylinder 302 is regulated by the first direct-acting overflow valve 201. The first three-position four-way solenoid reversing valve 203YA2 is energized. The system pressure of the loading cylinder 303 is regulated by the second direct-acting overflow valve 202, and finally different load outputs of the loading cylinder 303 are achieved to adapt to different load conditions of the test cylinder 305.

[0103] The force sensor 303 is installed between the loading cylinder 302 and the test cylinder 305, and is used to detect the piston seal friction and load force. The displacement sensor 304 is used to detect the displacement change of the piston rod of the test cylinder 305, and the buffering performance of the test cylinder 305 is measured according to the displacement time function. The first pressure sensor 206 is used for the inlet pressure of the loading cylinder 302. The second pressure sensor 306 is used to monitor the pressure of the buffer chamber 305-4 of the test cylinder 305. The size of this pressure data can be converted into the size of the impact force generated by the fluid itself in the chamber during the buffer stage. The third pressure sensor 307 is used to monitor the outlet pressure of the test cylinder 305. The controller 403 transmits the data collected by the above-mentioned data acquisition module through the control line 402, monitors the working condition of the test system in real time and processes the data.

[0104] The other parts of this embodiment are the same as those of the above-mentioned embodiment 1, and thus will not be described in detail.

[0105] Embodiment 3:

[0106] This embodiment is based on any one of the above embodiments 1 to 2. Figure 1 As shown, the specific structure of the power source module 1 is described.

[0107] The power source module 1 includes an oil level sensor 101, a filter 102, an oil tank 103, a first electric piston pump 104, a second electric piston pump 105, a first check valve 106, a proportional relief valve 107, a first two-position two-way electromagnetic reversing valve 108, a second check valve 109 and a third check valve 110;

[0108] The oil level sensor 101 is arranged on the oil tank 103;

[0109] The first electric plunger pump 104 is connected to the three-position four-way electromagnetic reversing valve 301 through the third one-way valve 110;

[0110] The second electric plunger pump 105 is connected to the throttling orifice 308 via a second one-way valve 109;

[0111] One end of the filter 102 is connected to the oil tank 103, and the other end is connected to the first electric plunger pump 104 and the second electric plunger pump 105;

[0112] One end of the proportional relief valve 107 is connected to the controller 403, and the other end is overlapped between the second one-way valve 109 and the throttling hole 308;

[0113] The first two-position two-way electromagnetic reversing valve 108 is connected to the controller 403 , the first one-way valve 106 , the proportional relief valve 107 , the second one-way valve 109 , and the throttling orifice 308 .

[0114] Working principle: The second one-way valve 109 and the third one-way valve 110 provided in this embodiment prevent the high-pressure hydraulic oil of the system from flowing back to the pump and damaging the oil pump. The first one-way valve 106 and the fourth one-way valve 205 ensure that the oil can only flow from the system back to the oil tank 103; when the first two-position two-way reversing valve 108 is energized, the return oil chamber 3058 of the test cylinder 305 is directly connected to the oil tank 103. At this time, the initial stage force of the force sensor 303 is the friction force of the piston seal of the test cylinder 305, and the value of the second pressure sensor 306 is the pressure change in the buffer chamber 3054 when the test cylinder 305 is unloaded; the proportional relief valve 107 can steplessly adjust the test system pressure to realize the simulation of different load conditions of the test cylinder 305.

[0115] The first electric piston pump 104, the YA3 of the second three-position four-way electromagnetic reversing valve 301 and the first two-position two-way reversing valve 108 are energized to adjust the piston positions of the test cylinder 305 and the loading cylinder 302 to the right end initial stage. Similarly, the second electric piston pump 105 and the second two-position two-way reversing valve 206 are energized to adjust the piston positions of the test cylinder 305 and the loading cylinder 302 to the right end initial stage.

[0116] The other parts of this embodiment are the same as any one of the above-mentioned embodiments 1-2, so they will not be repeated here.

[0117] Embodiment 4:

[0118] This embodiment is based on any one of the above embodiments 1 to 3. Figure 1 , Figure 3 As shown, the specific structure of the load force adjustment module 2 is described.

[0119] The load force regulating module 2 includes a first direct-acting relief valve 201, a second direct-acting relief valve 202, a first three-position four-way electromagnetic reversing valve 203, a third direct-acting relief valve 204, a fourth one-way valve 205, a second two-position two-way electromagnetic reversing valve 206 and a first pressure sensor 207;

[0120] The first direct-acting relief valve 201 and the second direct-acting relief valve 202 are connected to the oil tank 103 and the first three-position four-way electromagnetic reversing valve 203;

[0121] The first three-position four-way electromagnetic reversing valve 203 is connected to the controller 403 via a control line 402;

[0122] The third direct-acting relief valve 204 is connected to the first three-position four-way solenoid reversing valve 203, the controller 403, the third one-way valve 110, and the second three-position four-way solenoid reversing valve 301;

[0123] The second two-position two-way electromagnetic reversing valve 206 is connected to the fourth one-way valve 205, the second three-position four-way electromagnetic reversing valve 301, the controller 403, and the loading cylinder 302;

[0124] One end of the first pressure sensor 207 is connected to the second two-position two-way electromagnetic reversing valve 206 and the loading cylinder 302 , and the other end is connected to the controller 403 through the control line 402 .

[0125] Working principle: The second two-position two-way reversing valve 206 provided in this embodiment is a system safety valve. When the first pressure sensor 207 detects that the test system pressure is overshot, the controller 403 controls the second two-position two-way reversing valve 206 to be energized, and the system pressure is directly released by the second two-position two-way reversing valve 206.

[0126] The other parts of this embodiment are the same as any one of the above-mentioned embodiments 1 to 3, so they will not be repeated here.

[0127] Embodiment 5:

[0128] This embodiment is based on any one of the above embodiments 1 to 4. Figure 1 , Figure 3 As shown, the electrical signal control module 4 also includes a human-computer interaction interface 401;

[0129] The human-computer interaction interface 401 is used to display system pressure data, system displacement data, and system thrust data in real time.

[0130] The other parts of this embodiment are the same as any one of the above-mentioned embodiments 1 to 4, so they are not repeated here.

[0131] Embodiment 6:

[0132] This embodiment, based on any one of the above embodiments 1 to 5, proposes a comprehensive test method for annular gap throttling hydraulic buffer device, which is implemented based on the above-mentioned comprehensive test system for annular gap throttling hydraulic buffer device. Figure 4 As shown, the specific steps include the following steps.

[0133] Step S1: Connect the force sensor 303 to the test cylinder 305 and the loading cylinder 302 through threads, and connect the hydraulic pipeline of the system, check whether the control line 402 is connected, debug the electrical signal control module 4, and perform necessary parameter settings.

[0134] Step S2: By controlling the operation of the first electric piston pump 104, the power supply of the second three-position four-way electromagnetic reversing valve 301, and the extension of the loading cylinder 302, the detection data of the force sensor 303 is obtained, and the piston positions of the test cylinder 305 and the loading cylinder 302 are adjusted to the initial stage at the right end to complete the piston seal friction test; the detection data of the force sensor 303 is the piston seal friction of the test cylinder 305.

[0135] The step S2 specifically includes the following steps:

[0136] Step S21: Control the first electric piston pump 104 to operate, the second three-position four-way electromagnetic reversing valve 301 to be powered on, and the loading cylinder 302 to extend;

[0137] Step S22: When the second three-position four-way electromagnetic reversing valve 301YA4 is powered on, the first two-position two-way electromagnetic reversing valve 108 is powered on, the oil return chamber 3058 of the test cylinder 305 is directly connected to the oil tank 103, the test cylinder 305 runs without load, and the acquired detection data of the force sensor 303 is used as the friction force of the piston seal of the test cylinder 305;

[0138] Step S23: Control the second three-position four-way electromagnetic reversing valve 301YA3 to be powered on, adjust the piston positions of the test cylinder 305 and the loading cylinder 302 to the right end initial stage, and complete the piston seal friction test.

[0139] Step S3: By controlling the operation of the first electric plunger pump 104 and powering on the first three-position four-way electromagnetic reversing valve 203, the displacement time function of the piston rod 3053 fed back by the displacement sensor 304 is analyzed, the buffering performance is analyzed, and the pressure time function fed back by the pressure sensor 306 is analyzed secondly to determine whether there is a sharp increase in pressure when the test cylinder 305 enters the buffering moment, and the pressure peak is converted into the impact force of the fluid in the buffer chamber to complete the buffering performance test.

[0140] Furthermore, the step S3 specifically includes the following steps:

[0141] Step S31: Control the first electric piston pump 104 to operate, and the first three-position four-way electromagnetic reversing valve 203YA4 to be powered on. The pressure of the loading cylinder 302 is adjusted by the third direct-acting relief valve 204. The piston rod of the loading cylinder 302 moves to the left, pushing the test cylinder 305 to move to the left. The load of the test cylinder 305 is adjusted by the proportional relief valve 107.

[0142] Step S32: According to the actual unloading pressure of the proportional relief valve 107, three pressure supplies are provided to the loading cylinder 302 through the first direct-acting relief valve 201, the second direct-acting relief valve 202 and the third direct-acting relief valve 204;

[0143] Step S33: When the test cylinder 305 reaches the end of the stroke, observe whether the speed of the piston rod 3053 of the test cylinder 305 is significantly slowed down, and whether the device vibrates or hits;

[0144] Step S34: Analyze the displacement time function of the piston rod 3053 of the test cylinder 305 fed back by the displacement sensor 304, analyze the buffering performance based on the time function, and analyze the pressure time function fed back by the second pressure sensor 306, and determine whether there is a sharp increase in pressure when the test cylinder 305 enters the buffering state based on the pressure time function, and convert the pressure peak into the impact force of the fluid in the buffer chamber.

[0145] Step S4: Replace the test cylinder 305 and throttling hole 308 with different structural sizes and repeat steps S1 to S3 to complete the performance analysis test of the remaining buffer structures, and comprehensively evaluate the end buffer performance of the hydraulic cylinder when the annular gap and the hole are combined for throttling according to the test result report.

[0146] The step S4 specifically comprises the following steps:

[0147] Step S41: Replace the annular gap throttling test cylinder 305 of different sizes and execute steps S1 to S3 to comprehensively evaluate the end buffer performance of the hydraulic cylinder when only the annular gap throttling is performed;

[0148] Step S42: Replace the test cylinder 305 with a hydraulic cylinder without buffering performance to execute steps S1 to S3, and replace the throttling orifices 308 with different structural sizes to comprehensively evaluate the end buffering performance of the hydraulic cylinder when only the orifice is throttled;

[0149] Step S43: Replace the annular gap throttling test cylinder 305 and the throttling orifice 308 with different structural sizes to execute steps S1 to S3, and comprehensively evaluate the end buffer performance of the hydraulic cylinder when the annular gap and the orifice are combined for throttling.

[0150] Step S5: After the test is completed, turn off the valve and power supply, tidy up the test bench, and analyze the test result report.

[0151] Working principle: This embodiment first debugs the installation process, then conducts a piston seal friction test, then a buffer performance test, and finally conducts performance analysis tests on other buffer structures, providing a comprehensive test method for an annular gap throttling hydraulic buffer device for key technical research such as the sealing rubber friction force and buffer chamber fluid impact force test in the annular gap throttling hydraulic buffer device, and realizing buffer performance tests on hydraulic cylinders of different structures, thereby providing a test platform for the prototype design and optimization of the annular gap throttling hydraulic buffer device, ensuring the feasibility of new products and effectively improving the overall R&D efficiency.

[0152] The other parts of this embodiment are the same as any one of the above-mentioned embodiments 1 to 5, so they will not be repeated here.

[0153] The above description is only a preferred embodiment of the present invention and does not limit the present invention in any form. Any simple modification or equivalent change made to the above embodiment based on the technical essence of the present invention shall fall within the protection scope of the present invention.

Claims

1. A comprehensive test system for annular gap throttling hydraulic buffer device, characterized in that: It comprises a power source module (1), a load force adjustment module (2), a buffer performance test module (3), and an electrical signal control module (4); The buffer performance test module (3) comprises a force sensor (303), a loading cylinder (302), a detachable test cylinder (305), and a detachable throttling orifice (308); The power source module (1) is connected to the buffer performance test module (3) via a hydraulic pipeline; The electrical signal control module (4) comprises a control circuit (402) and a controller (403); The load force adjustment module (2) is connected to the buffer performance testing module (3) via a hydraulic pipeline; The electric signal control module (4) is connected to the power source module (1), the load force adjustment module (2) and the buffer performance test module (3); The force sensor (303) is arranged between the loading cylinder (302) and the test cylinder (305); The throttling hole (308) is arranged between the test cylinder (305) and the power source module (1).

2. A comprehensive test system for annular gap throttling hydraulic buffer device according to claim 1, characterized in that: The test cylinder (305) comprises an oil inlet chamber (3051), an outer cylinder (3052), a test cylinder piston rod (3053), a buffer chamber (3054), a buffer cone surface (3056), a buffer gap (3057), and an oil return chamber (3058); The oil inlet chamber (3051), the buffer chamber (3054), and the oil return chamber (3058) are all arranged in the outer cylinder (3052); The oil return chamber (3058) is connected to the power source module (1); The buffer starting section of the buffer chamber (3054) is provided with a buffer cone surface (3056), and the buffer chamber (3054) is connected to the oil return chamber (3058) through a buffer gap (3057).

3. A comprehensive test system for annular gap throttling hydraulic buffer device according to claim 2, characterized in that: The length of the buffer cone surface (3056) is half of the buffer process (3055) of the buffer cavity (3054).

4. A comprehensive test system for annular gap throttling hydraulic buffer device according to claim 3, characterized in that: The buffer gap (3057) is an annular gap throttling.

5. The comprehensive test system for annular gap throttling hydraulic buffer device according to claim 1 is characterized in that: The buffer performance test module (3) further comprises a second three-position four-way electromagnetic reversing valve (301), a displacement sensor (304), a second pressure sensor (306), and a third pressure sensor (307); The three-position four-way electromagnetic reversing valve (301) is connected to the power source module (1), the loading cylinder (302), and the load force adjustment module (2); One end of the displacement sensor (304) is connected to the force sensor (303), and the other end is connected to the controller (403); one end of the second pressure sensor (306) is connected to the controller (403), and the other end is connected to the test cylinder (305); One end of the third pressure sensor (307) is overlapped between the test cylinder (305) and the throttling hole (308), and the other end is connected to the controller (403).

6. A comprehensive test system for annular gap throttling hydraulic buffer device according to claim 5, characterized in that: The power source module (1) comprises an oil level sensor (101), a filter (102), an oil tank (103), a first electric piston pump (104), a second electric piston pump (105), a first check valve (106), a proportional relief valve (107), a first two-position two-way electromagnetic reversing valve (108), a second check valve (109) and a third check valve (110); The oil level sensor (101) is arranged on the oil tank (103); The first electric piston pump (104) is connected to the three-position four-way electromagnetic reversing valve (301) via a third one-way valve (110); the second electric piston pump (105) is connected to the throttling orifice (308) via a second one-way valve (109); One end of the filter (102) is connected to the oil tank (103), and the other end is connected to the first electric plunger pump (104) and the second electric plunger pump (105); One end of the proportional relief valve (107) is connected to the controller (403), and the other end is overlapped between the second one-way valve (109) and the throttling orifice (308); The first two-position two-way electromagnetic reversing valve (108) is connected to the controller (403), the first one-way valve (106), the proportional relief valve (107), the second one-way valve (109), and the throttling orifice (308).

7. A comprehensive test system for annular gap throttling hydraulic buffer device according to claim 6, characterized in that: The load force adjustment module (2) comprises a first direct-acting relief valve (201), a second direct-acting relief valve (202), a first three-position four-way electromagnetic reversing valve (203), a third direct-acting relief valve (204), a fourth one-way valve (205), a second two-position two-way electromagnetic reversing valve (206) and a first pressure sensor (207); The first direct-acting relief valve (201) and the second direct-acting relief valve (202) are connected to the oil tank (103) and the first three-position four-way electromagnetic reversing valve (203); The first three-position four-way electromagnetic reversing valve (203) is connected to a controller (403) via a control line (402); The third direct-acting relief valve (204) is connected to the first three-position four-way electromagnetic reversing valve (203), the controller (403), the third one-way valve (110), and the second three-position four-way electromagnetic reversing valve (301); The second two-position two-way electromagnetic reversing valve (206) is connected to the fourth one-way valve (205), the second three-position four-way electromagnetic reversing valve (301), the controller (403), and the loading cylinder (302); One end of the first pressure sensor (207) is overlapped with the second two-position two-way electromagnetic reversing valve (206) and connected to the loading cylinder (302), and the other end is connected to the controller (403) through the control line (402).

8. The comprehensive test system for annular gap throttling hydraulic buffer device according to claim 1 is characterized in that: The electrical signal control module (4) further comprises a human-computer interaction interface (401); The human-computer interaction interface (401) is used to display system pressure data, system displacement data, and system thrust data in real time.

9. A comprehensive test method for annular gap throttling hydraulic buffer device, implemented based on the comprehensive test system for annular gap throttling hydraulic buffer device according to claim 1, characterized in that: The specific steps include: Step S1: Connect the force sensor (303) to the test cylinder (305) and the loading cylinder (302) through threads, connect the hydraulic pipeline of the system, check whether the control line (402) is connected, debug the electrical signal control module (4), and perform necessary parameter settings; Step S2: by controlling the first electric piston pump (104) to operate, the second three-position four-way electromagnetic reversing valve (301) to be powered on, and the loading cylinder (302) to be extended, the force sensor (303) detection data is obtained, and the piston positions of the test cylinder (305) and the loading cylinder (302) are adjusted to the right end initial stage, so as to complete the piston seal friction force test; the force sensor (303) detection data is the piston seal friction force of the test cylinder (305); Step S3: by controlling the operation of the first electric piston pump (104) and the power-on of the first three-position four-way electromagnetic reversing valve (203), the displacement time function of the piston rod (3053) fed back by the displacement sensor (304) is analyzed to analyze the buffering performance, and the pressure time function fed back by the pressure sensor (306) is analyzed to determine whether there is a sharp increase in pressure at the moment when the test cylinder (305) enters the buffering state, and the pressure peak is converted into the impact force of the fluid in the buffer chamber to complete the buffering performance test; Step S4: Replace the test cylinder (305) and throttling orifice (308) of different structural sizes and repeat steps S1 to S3 to complete the performance analysis test of the remaining buffer structures, and comprehensively evaluate the end buffer performance of the hydraulic cylinder when the annular gap and the orifice are combined for throttling according to the test result report.

10. A comprehensive test system for annular gap throttling hydraulic buffer device according to claim 9, characterized in that: The step S2 specifically includes the following steps: Step S21: Control the first electric piston pump (104) to operate, the second three-position four-way electromagnetic reversing valve (301) to be powered on, and the loading cylinder (302) to extend; Step S22: When the second three-position four-way electromagnetic reversing valve (301) YA4 is powered on, the first two-position two-way electromagnetic reversing valve (108) is powered on, the oil return chamber (3058) of the test cylinder (305) is directly connected to the oil tank (103), the test cylinder (305) runs without load, and the acquired detection data of the force sensor (303) is used as the friction force of the piston seal of the test cylinder (305); Step S23: Control the second three-position four-way electromagnetic reversing valve (301) YA3 to be powered on, adjust the piston positions of the test cylinder (305) and the loading cylinder (302) to the right end initial stage, and complete the piston seal friction test.

11. The annular gap throttling hydraulic buffer device comprehensive test system according to claim 9 is characterized in that: The step S3 specifically comprises the following steps: Step S31: Control the first electric piston pump (104) to operate, the first three-position four-way electromagnetic reversing valve (203) YA4 to be powered on, the pressure of the loading cylinder (302) is adjusted by the third direct-acting relief valve (204), the piston rod of the loading cylinder (302) moves to the left, pushing the test cylinder (305) to move to the left, and the load of the test cylinder (305) is adjusted by the proportional relief valve (107); Step S32: providing three pressure supplies to the loading cylinder (302) through the first direct-acting relief valve (201), the second direct-acting relief valve (202) and the third direct-acting relief valve (204) according to the actual unloading pressure of the proportional relief valve (107); Step S33: When the test cylinder (305) reaches the end of the stroke, observe whether the speed of the piston rod (3053) of the test cylinder (305) is significantly slowed down, and whether the device has vibration or impact; Step S34: Analyze the displacement time function of the piston rod (3053) of the test cylinder (305) fed back by the displacement sensor (304), analyze the buffering performance based on the time function, and analyze the pressure time function fed back by the second pressure sensor (306), and determine whether there is a sharp increase in pressure when the test cylinder (305) enters the buffering state based on the pressure time function, and convert the pressure peak into the impact force of the fluid in the buffer chamber.

12. The annular gap throttling hydraulic buffer device comprehensive test system according to claim 9 is characterized in that: The step S4 specifically comprises the following steps: Step S41: replacing annular gap throttling test cylinders (305) of different sizes to execute steps S1 to S3, and comprehensively evaluating the end buffering performance of the hydraulic cylinder when only the annular gap throttling is performed; Step S42: Replace the test cylinder (305) with a hydraulic cylinder without buffering performance, execute steps S1 to S3, and replace the throttling orifices (308) with different structural sizes, and comprehensively evaluate the end buffering performance of the hydraulic cylinder when only the orifice is throttled; Step S43: Replace the annular gap throttling test cylinder (305) and the throttling orifice (308) of different structural sizes to execute steps S1 to S3, and comprehensively evaluate the end buffer performance of the hydraulic cylinder when the annular gap and the orifice are combined for throttling.

Images