Hydraulic cylinder working condition simulation test device, control system and method

Abstract

The present invention relates to the field of hydraulic cylinder performance testing, and provides a hydraulic cylinder working condition simulation test device, a control system and a method thereof. A hydraulic cylinder working condition simulation test device includes: a first loading cylinder and a second loading cylinder, the first loading cylinder is connected to the hydraulic cylinder to be tested, and the axes coincide; the second loading cylinder is connected to the hydraulic cylinder to be tested, and the axes are perpendicular; the second loading cylinder can apply a dynamic load to the hydraulic cylinder to be tested. This solves the defect in the prior art that it is impossible to radially apply dynamic eccentric load to the hydraulic cylinder to test the anti-eccentric load performance. In the hydraulic cylinder working condition simulation test device provided by the present invention, a second loading cylinder is arranged radially of the hydraulic cylinder to test the anti-eccentric load capability; the second loading cylinder can simulate the situation where the hydraulic cylinder to be tested is subjected to a dynamic radial load, thereby meeting a variety of performance tests of hydraulic cylinders with different needs, and has a wide range of applications.

Description

Technical Field

[0001] The present invention relates to the technical field of hydraulic cylinder performance testing, and in particular to a hydraulic cylinder working condition simulation test device, a control system and a method thereof. Background Art

[0002] Currently, most hydraulic cylinders are tested according to GB / T 15622-2005, "Hydraulic Cylinder Test Methods," which covers nine test items, including trial runs, starting pressure characteristics tests, and pressure resistance tests. These tests do not include eccentric load simulation tests. Analysis of faulty components, such as pump truck outrigger cylinders, crane outrigger cylinders, and excavator bucket cylinders, revealed that misalignment between the cylinder's installation position and the load's trajectory is common in actual operating conditions. Eccentric load conditions are a key factor in many failures, including internal and external leakage, piston rod fracture, and cylinder wall damage. For outrigger cylinders in pump trucks, in particular, the immense impact generated by the momentary reversal of the main engine during continuous pumping can cause periodic eccentric load conditions. Internal or external leakage in these cylinders can easily lead to safety incidents such as rollover. Therefore, simulating eccentric load conditions to assess hydraulic cylinders' resistance to eccentric loads is essential and valuable.

[0003] However, the existing hydraulic cylinder working condition simulation test device is unable to apply a dynamic eccentric load to the hydraulic cylinder in the radial direction to test the anti-eccentric load performance. Summary of the Invention

[0004] The present invention provides a hydraulic cylinder working condition simulation test device, a control system and a method thereof, which are used to solve the defect in the prior art that it is impossible to apply a dynamic eccentric load to the hydraulic cylinder in the radial direction to test the anti-eccentric load performance. By setting a first loading cylinder in the axial direction of the hydraulic cylinder being tested to apply an axial load, and setting a second loading cylinder in the radial direction of the hydraulic cylinder being tested to apply a dynamic radial load, the anti-eccentric load performance test of the hydraulic cylinder is achieved.

[0005] The present invention provides a hydraulic cylinder working condition simulation test device, comprising:

[0006] a first loading cylinder, wherein a first telescopic rod of the first loading cylinder is used to connect with the telescopic rod of the hydraulic cylinder under test, and the axis of the first telescopic rod coincides with the axis of the telescopic rod of the hydraulic cylinder under test;

[0007] a second loading cylinder, wherein a second telescopic rod of the second loading cylinder is used to connect with the telescopic rod of the tested hydraulic cylinder, and in an initial state, the second telescopic rod is perpendicular to the axis of the telescopic rod of the tested hydraulic cylinder;

[0008] Wherein, the second loading cylinder is used to apply a dynamic load to the telescopic rod of the tested hydraulic cylinder.

[0009] The hydraulic cylinder working condition simulation test device provided by the present invention further includes a box body and a movable frame, wherein the movable frame is arranged on the box body and can be displaced on the box body;

[0010] One side of the box is connected to the tested hydraulic cylinder, and the other side of the box is connected to the first loading cylinder. The telescopic rod of the tested hydraulic cylinder and the first telescopic rod are placed in the box;

[0011] The cylinder body of the second loading cylinder is installed on the moving frame.

[0012] The hydraulic cylinder working condition simulation test device provided according to the present invention further includes an articulated shaft, the telescopic rod of the tested hydraulic cylinder and the second telescopic rod are hinged to one end of the articulated shaft, and the first telescopic rod is hinged to the other end of the articulated shaft.

[0013] The present invention also provides a hydraulic cylinder working condition simulation test control system, comprising a first hydraulic control circuit, a second hydraulic control circuit, a third hydraulic control circuit and the above-mentioned hydraulic cylinder working condition simulation test device;

[0014] Wherein, the first hydraulic control circuit is connected to the tested hydraulic cylinder, the second hydraulic control circuit is connected to the first loading cylinder, and the third hydraulic control circuit is connected to the second loading cylinder.

[0015] According to the hydraulic cylinder working condition simulation test control system provided by the present invention, the first hydraulic control circuit includes a first hydraulic pump and a first reversing valve, and the first hydraulic pump is connected to the first reversing valve;

[0016] Wherein, a quick-connect connector is provided between the first reversing valve and the oil ports of the rod chamber and the rodless chamber of the hydraulic cylinder to be tested.

[0017] The hydraulic cylinder working condition simulation test control system provided by the present invention further includes a weighing assembly and an oil pipe, one end of the oil pipe is arranged between the tested hydraulic cylinder and the quick-connect connector, and the other end of the oil pipe is connected to the weighing assembly;

[0018] Wherein, the oil pipe is provided with a first stop valve.

[0019] According to the hydraulic cylinder working condition simulation test control system provided by the present invention, the second hydraulic control circuit includes a second shut-off valve, and the second shut-off valve is provided between the first loading cylinder and the oil tank of the hydraulic cylinder working condition simulation test control system.

[0020] According to the hydraulic cylinder working condition simulation test control system provided by the present invention, the second hydraulic control circuit further includes a relief valve, and the relief valve is arranged between the oil tank and the second stop valve.

[0021] The present invention also provides a hydraulic cylinder working condition simulation test method, comprising:

[0022] Setting the axial loading force of the first loading cylinder;

[0023] Select the loading force variation curve based on the performance requirements of the hydraulic cylinder being tested;

[0024] Based on the selected loading force variation curve, controlling the action of the second loading cylinder for radial loading;

[0025] supplying oil to the first chamber of the tested hydraulic cylinder;

[0026] The leaked oil of the second chamber of the tested hydraulic cylinder is obtained to obtain the internal leakage amount.

[0027] According to the hydraulic cylinder working condition simulation test method provided by the present invention, before setting the axial loading force of the first loading cylinder, the method further includes:

[0028] Lock the hydraulic cylinder under test;

[0029] supplying oil to the first chamber of the tested hydraulic cylinder;

[0030] The leaked oil of the second chamber of the tested hydraulic cylinder is obtained to obtain an initial internal leakage amount.

[0031] The hydraulic cylinder working condition simulation test device provided by the present invention simulates the working condition of the hydraulic cylinder being tested under different loads by arranging a first loading cylinder in the axial direction of the hydraulic cylinder being tested, and simulates the working condition of the hydraulic cylinder being tested being not in the same axis as the load it is subjected to, that is, testing the anti-eccentric load capability; the second loading cylinder can simulate the condition of the hydraulic cylinder being tested being subjected to dynamic radial load, thereby meeting various performance tests of hydraulic cylinders with different needs, and has a wide range of applications.

[0032] Furthermore, in the hydraulic cylinder working condition simulation test control system provided by the present invention, since it has the hydraulic cylinder working condition simulation test device as described above, it also has the various advantages as described above. The hydraulic cylinder working condition simulation test method is a control method corresponding to the hydraulic cylinder working condition simulation test device, and therefore also has the advantages of the hydraulic cylinder working condition simulation test device. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] In order to more clearly illustrate the technical solutions in the present invention or the prior art, a brief introduction is given below to the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0034] Figure 1 It is a structural schematic diagram of the hydraulic cylinder working condition simulation test device provided by the present invention;

[0035] Figure 2 This is a schematic diagram of the hydraulic cylinder working condition simulation test control system provided by the present invention;

[0036] Figure 3 is a loading force variation curve diagram of the dynamic load of the second loading cylinder provided by the present invention;

[0037] Figure 4 This is one of the flow charts of the hydraulic cylinder working condition simulation test method provided by the present invention;

[0038] Figure 5 This is the second flow chart of the hydraulic cylinder working condition simulation test method provided by the present invention.

[0039] Reference numerals:

[0040] 100: Hydraulic cylinder under test; 110: First hydraulic control circuit; 111: First hydraulic pump; 112: First reversing valve; 113: Quick connector; 114: First shut-off valve; 120: Weighing assembly; 130: Fuel tank;

[0041] 200: second loading cylinder; 201: second telescopic rod; 210: third hydraulic control circuit; 211: second hydraulic pump; 212: second reversing valve; 213: first speed regulating valve; 214: second speed regulating valve; 215: third overflow valve;

[0042] 300: first loading cylinder; 301: first telescopic rod; 310: second hydraulic control circuit; 311: second shut-off valve; 312: first relief valve; 313: second relief valve; 314: third oil pipe; 315: fourth oil pipe; 316: fifth oil pipe; 317: sixth oil pipe;

[0043] 400: Box body; 401: Mobile frame; 402: Articulated shaft. DETAILED DESCRIPTION

[0044] To make the objectives, technical solutions, and advantages of the present invention more clear, the technical solutions of the present invention will be clearly and completely described below in conjunction with the accompanying drawings. Obviously, the embodiments described are only some of the embodiments of the present invention, not all of them. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts shall fall within the scope of protection of the present invention.

[0045] In the description of the embodiments of the present invention, it should be noted that the terms "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating directions or positional relationships, are based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the embodiments of the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific direction, be constructed and operate in a specific direction. Therefore, they should not be understood as limiting the embodiments of the present invention. In addition, the terms "first", "second", and "third" are used for descriptive purposes only and should not be understood as indicating or implying relative importance.

[0046] In the description of the embodiments of the present invention, it should be noted that, unless otherwise specified or limited, the terms "connected" and "connection" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integral connections; mechanical connections, electrical connections; and direct connections or indirect connections through an intermediary. Those skilled in the art will understand the specific meanings of the above terms in the embodiments of the present invention based on the specific circumstances.

[0047] In the description of this specification, the reference terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" mean that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the embodiment of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art can combine and combine different embodiments or examples described in this specification and features of different embodiments or examples without contradiction.

[0048] The following combination Figures 1 to 5 It should be understood that the following description is merely an illustrative embodiment of the present invention and does not constitute a limitation on the present invention.

[0049] like Figure 1 As shown, the present invention provides a hydraulic cylinder working condition simulation test device, including: a first loading cylinder 300 applying axial force to the tested hydraulic cylinder 100, and a second loading cylinder 200 applying radial force to the tested hydraulic cylinder 100.

[0050] Specifically, the first telescopic rod 301 of the first loading cylinder 300 is used to connect with the telescopic rod of the hydraulic cylinder 100 under test, and the first telescopic rod 301 coincides with the axis of the telescopic rod of the hydraulic cylinder 100 under test; the second telescopic rod 201 of the second loading cylinder 200 is used to connect with the telescopic rod of the hydraulic cylinder 100 under test, and in the initial state, the second telescopic rod 201 is perpendicular to the axis of the telescopic rod of the hydraulic cylinder 100 under test; wherein, the second loading cylinder 200 is used to apply a dynamic load to the telescopic rod of the hydraulic cylinder 100 under test.

[0051] The axial force applied by the first loading cylinder 300 corresponds to the load on the tested hydraulic cylinder 100, while the radial force applied by the second loading cylinder 200 corresponds to the eccentric load experienced by the tested hydraulic cylinder 100 during operation. In other words, the radial force applied by the second loading cylinder 200 to the tested hydraulic cylinder 100 is equivalent to a condition in which the tested hydraulic cylinder 100 is not coaxial with the load's trajectory. The dynamic load provided by the second loading cylinder 200 can be a constant force after reaching a certain load point, a unidirectional pulsating force, or a bidirectional sinusoidal force.

[0052] For example, under the first working condition: during the extension or retraction of the telescopic rod of the tested hydraulic cylinder 100, by controlling the sealing of the oil ports of the rod chamber and the rodless chamber of the first loading cylinder 300, the internal leakage of the tested hydraulic cylinder 100 can be measured at a specified position, that is, the internal leakage of the tested hydraulic cylinder 100 under the top pressure maintaining working condition can be measured.

[0053] In the second working condition, the oil ports of the rod chamber and the rodless chamber of the first loading cylinder 300 are blocked, and a radial dynamic load is applied through the second loading cylinder 200, and the internal leakage of the two chambers of the tested hydraulic cylinder 100 is measured respectively.

[0054] In the third operating condition, the oil return ports of the rod chamber and rodless chamber of the first loading cylinder 300 are set to open pressure, thereby applying a certain load to the hydraulic cylinder 100 under test via the first loading cylinder 300. The hydraulic cylinder 100 under test then performs an extension and retraction motion. After the cumulative extension and retraction motion reaches a preset value, the internal leakage measurement for top-pressure maintenance is performed. For example, when the cumulative number of extension and retraction motions reaches 200,000 or the cumulative travel reaches 100 kilometers, the internal leakage measurement for top-pressure maintenance is complete.

[0055] In the fourth operating condition, the oil return ports of the rod chamber and rodless chamber of the first loading cylinder 300 are set to open pressure. This means that a certain load is applied to the hydraulic cylinder 100 under test via the first loading cylinder 300. Simultaneously, a dynamic load is applied via the second loading cylinder 200. The hydraulic cylinder 100 under test is extended and retracted while under axial and radial loads. After the cumulative extension and retraction motions of the hydraulic cylinder 100 under test reach a preset value, the internal leakage measurement for top pressure maintenance is performed. For example, when the cumulative number of extension and retraction motions reaches 200,000 or the cumulative travel distance reaches 100 kilometers, the internal leakage measurement for top eccentric load is completed.

[0056] Continue to refer Figure 1 In one embodiment of the present invention, the hydraulic cylinder working condition simulation test device also includes a box 400 and a movable frame 401. The movable frame 401 is set on the box 400 and can be shifted on the box 400; one side of the box 400 is connected to the tested hydraulic cylinder 100, and the other side of the box 400 is connected to the first loading cylinder 300. The telescopic rod of the tested hydraulic cylinder 100 and the first telescopic rod 301 are placed in the box 400; the cylinder body of the second loading cylinder 200 is connected to the movable frame 401.

[0057] In other words, the housing 400 includes an inner cavity, sidewalls, and an open upper surface. The movable frame 401 is disposed on the upper surface, for example, the movable frame 401 is movable on the upper surface. The cylinder body of the tested hydraulic cylinder 100 is connected to the sidewall, and the cylinder body of the first loading cylinder 300 is connected to the sidewall. The first loading cylinder 300 and the tested hydraulic cylinder 100 are positioned opposite each other, and the cylinder body of the first loading cylinder 300 is fixedly connected to the sidewall of the housing 400. The telescopic rod of the tested hydraulic cylinder 100 and the first telescopic rod 301 are positioned within the inner cavity. The linear movement of the telescopic rod of the tested hydraulic cylinder 100 can drive the linear movement of the first telescopic rod 301. Under test conditions, the movement of the first telescopic rod 301 and the second telescopic rod 201 is minimal.

[0058] The cylinder body of the second loading cylinder 200 is connected to the movable frame 401, and the second telescopic rod 201 is connected to the telescopic rod of the hydraulic cylinder 100 being tested. The movable frame 401 can be locked at a designated position on the upper surface of the housing 400. For example, while the telescopic rod of the hydraulic cylinder 100 being tested drives the first telescopic rod 301 to move, the movable frame 401 drives the second loading cylinder 200 to move along the axis of the telescopic rod of the hydraulic cylinder 100 being tested and the first telescopic rod 301, without the second loading cylinder 200 applying a loading force. This allows for a top-to-bottom test mode to be implemented without disassembling the second loading cylinder 200. The second loading cylinder 200 can adjust the angle of the radial loading force applied to the telescopic rod of the hydraulic cylinder 100 being tested.

[0059] The box 400 has a good safety protection function. When the tested hydraulic cylinder 100 fails or the hydraulic component fails, the box 400 can play a good protective role. In the initial state, the axis of the second loading cylinder 200 coincides with the central axis of the moving frame 401.

[0060] For example, the position of the movable frame 401 on the upper surface of the housing 400 can be adjusted using bolts. The cylinder body of the second loading cylinder 200 is connected to the movable frame 401 via a trunnion. The second loading cylinder 200 is capable of slight swinging during the reciprocating motion of the tested hydraulic cylinder 100. The swing amplitude is primarily limited by the loading force of the first loading cylinder; of course, it is also affected by the clearance between the telescopic rod and guide sleeve, and between the cylinder barrel and piston of the tested hydraulic cylinder. Swinging angles of 30 degrees or less are generally considered to be slight swing.

[0061] Furthermore, in another embodiment of the present invention, the hydraulic cylinder operating condition simulation test apparatus further includes an articulation axis 402. The telescopic rod and the second telescopic rod 201 of the tested hydraulic cylinder 100 are hingedly connected to one end of the articulation axis 402, while the first telescopic rod 301 is hingedly connected to the other end of the articulation axis 402. In other words, the first telescopic rod 301 is connected to the telescopic rod of the tested hydraulic cylinder 100 via the articulation axis 402, and the radial loading force of the second telescopic rod 201 acts directly on the telescopic rod of the tested hydraulic cylinder 100. This prevents the radial loading force applied by the second telescopic rod 201 from causing deformation of the first telescopic rod 301 or causing cylinder failure, thereby preventing the load from being constant.

[0062] like Figure 2 As shown, the present invention also provides a hydraulic cylinder working condition simulation test control system, including a first hydraulic control circuit 110, a second hydraulic control circuit 310, a third hydraulic control circuit 210 and the hydraulic cylinder working condition simulation test device of the above embodiment; wherein, the first hydraulic control circuit 110 is connected to the tested hydraulic cylinder 100, the second hydraulic control circuit 310 is connected to the first loading cylinder 300, and the third hydraulic control circuit 210 is connected to the second loading cylinder 200.

[0063] Specifically, the first hydraulic control circuit 110 is used to control the extension and retraction of the hydraulic cylinder 100 under test, the second hydraulic control circuit 310 is used to control the load applied by the first loading cylinder 300 to the hydraulic cylinder 100 under test, and the third hydraulic control circuit 210 is used to control the extension and retraction of the second loading cylinder 200. For example, the second hydraulic control circuit 310 drives the second telescopic rod 201 to extend, applying radial pressure to the hydraulic cylinder 100 under test; the second hydraulic control circuit 310 drives the second telescopic rod 201 to retract, applying radial tension to the hydraulic cylinder 100 under test. The second hydraulic control circuit 310 and the third hydraulic control circuit 210 can be activated simultaneously or independently. In other words, the first loading cylinder 300 and the second loading cylinder 200 can apply force to the hydraulic cylinder 100 under test simultaneously or independently.

[0064] The hydraulic cylinder working condition simulation test control system of the hydraulic cylinder working condition simulation test device can realize all 9 basic performance test items in the national standard GB / T15622-2005 "Hydraulic Cylinder", namely a. trial operation, b. starting pressure characteristic test, c. pressure resistance test, d. durability test, e. leakage test, f. buffer test, g. load efficiency test, h. high temperature test and i. stroke detection.

[0065] Continue to refer Figure 2 In an optional embodiment of the present invention, the first hydraulic control circuit 110 includes a first hydraulic pump 111 and a first reversing valve 112, and the first hydraulic pump 111 is connected to the first reversing valve 112; wherein, a quick-connect connector 113 is provided between the first reversing valve 112 and the rod chamber and rodless chamber of the hydraulic cylinder 100 under test. In other words, the first hydraulic control circuit 110 is connected to the rod chamber and rodless chamber of the hydraulic cylinder 100 under test via the quick-connect connector 113, which is convenient for plugging and unplugging. The first reversing valve 112 can be a three-position four-way solenoid reversing valve or a three-position four-way manual reversing valve, and the extension and retraction of the hydraulic cylinder 100 under test can be achieved by switching the first reversing valve 112. wherein, the quick-connect connector 113 of the rod chamber or the rodless chamber of the hydraulic cylinder 100 under test can be disconnected separately according to the test requirements.

[0066] In addition, in another optional embodiment of the present invention, the hydraulic cylinder working condition simulation test control system also includes a weighing component 120 and an oil pipe, one end of the oil pipe is arranged between the tested hydraulic cylinder 100 and the quick-connect connector 113, and the other end of the oil pipe is connected to the weighing component 120; wherein, the oil pipe is provided with a first stop valve 114.

[0067] Specifically, the first reversing valve 112 includes a first oil outlet and a second oil outlet. The first oil outlet is connected to the rodless chamber of the hydraulic cylinder 100 under test via a quick-connect connector 113, while the second oil outlet is connected to the rod chamber of the hydraulic cylinder 100 under test via a quick-connect connector 113. A first oil pipe is connected between the rodless chamber and the quick-connect connector 113, with one end of the first oil pipe communicating with the rodless chamber and the other end communicating with the weighing assembly 120. A second oil pipe is connected between the rod chamber and the quick-connect connector 113, with one end of the second oil pipe communicating with the rod chamber and the other end communicating with the weighing assembly 120. Both the first and second oil pipes are provided with a first shut-off valve 114.

[0068] For example, if it is necessary to detect the internal leakage of the rod chamber of the hydraulic cylinder 100 being tested, the quick connector 113 between the second oil outlet and the rod chamber should be unplugged, and the first stop valve 114 on the second oil pipe should be opened. Similarly, if it is necessary to detect the internal leakage of the rodless chamber of the hydraulic cylinder 100 being tested, the quick connector 113 between the first oil outlet and the rodless chamber should be unplugged, and the first stop valve 114 on the first oil pipe should be opened. The amount of oil flowing into the weighing component 120 is the internal leakage, wherein the weighing component 120 can be a container and an electronic scale to meet the measurement requirements of leakage within different ranges; it can be a measuring cup, and the internal leakage can be directly read; it can be a flow meter, and the instantaneous value of the internal leakage can be read, which is suitable for occasions where the internal leakage increases; it can be a metering oil cylinder, and the internal leakage can be effectively quantified, which is suitable for occasions where the internal leakage increases.

[0069] Of course, the first hydraulic control circuit 110 further includes a one-way throttle valve provided between the quick-connect connector 113 and the first reversing valve 112 .

[0070] Furthermore, in other embodiments of the present invention, the second hydraulic control circuit 310 includes a second shut-off valve 311 , and the second shut-off valve 311 is provided between the first loading cylinder 300 and the oil tank 130 of the hydraulic cylinder working condition simulation test control system.

[0071] Specifically, a second shutoff valve 311 is installed on the pipeline between the rod chamber of the first loading cylinder 300 and the oil tank 130. A second shutoff valve 311 is also installed on the pipeline between the rodless chamber of the first loading cylinder 300 and the oil tank 130. In other words, the second hydraulic control circuit 310 lacks a hydraulic pump. Instead, the first loading cylinder 300 draws oil from and draws oil from the first loading cylinder 300 using the pressure from the tested hydraulic cylinder 100. In other words, the second hydraulic control circuit 310 connects the rod chamber and the rodless chamber of the first loading cylinder 300 via two second shutoff valves 311.

[0072] Continue to refer Figure 2 In a preferred embodiment of the present invention, the second hydraulic control circuit 310 further includes a relief valve, which is disposed between the oil tank 130 and the second shut-off valve 311. The relief valve may be an electromagnetic relief valve.

[0073] In other words, a second shutoff valve 311 is installed at the oil port of the rod chamber of the first loading cylinder 300. A third oil pipe 314 is provided between this second shutoff valve 311 and the oil tank 130, and a first relief valve 312 is installed on this third oil pipe 314. Similarly, another second shutoff valve 311 is installed at the oil port of the rodless chamber of the first loading cylinder 300. A fourth oil pipe 315 is provided between this shutoff valve and the oil tank 130, and a second relief valve 313 is installed on this fourth oil pipe 315. Furthermore, a first check valve is installed on the third oil pipe 314, located between the second shutoff valve 311 and the first relief valve 312. The first check valve only allows hydraulic oil to flow from the rod chamber into the oil tank 130. A second check valve is installed on the fourth oil pipe 315, located between the second shutoff valve 311 and the second relief valve 313. The second check valve only allows hydraulic oil to flow from the rodless chamber into the oil tank 130.

[0074] Furthermore, a fifth oil pipe 316 is arranged between the second stop valve 311 of the rod chamber oil port and the oil tank 130, and a third one-way valve is arranged on the fifth oil pipe 316, and the third one-way valve only allows hydraulic oil to flow from the oil tank 130 into the rod chamber; a sixth oil pipe 317 is arranged between the second stop valve 311 of the rodless chamber oil port and the oil tank 130, and a fourth one-way valve is arranged on the sixth oil pipe 317, and the fourth one-way valve only allows hydraulic oil to flow from the oil tank 130 into the rodless chamber.

[0075] That is, when the first hydraulic control circuit 110 drives the telescopic rod of the tested hydraulic cylinder 100 to extend, the first loading cylinder 300 retracts under the force of the tested hydraulic cylinder 100, opening the second shut-off valve 311 of the rodless chamber oil port of the first loading cylinder 300 and the second shut-off valve 311 of the rodless chamber oil port of the first loading cylinder 300. The hydraulic oil in the rodless chamber of the first loading cylinder 300 flows through the second shut-off valve 311, the second check valve, and the second relief valve 313, returning to the oil tank 130. Specifically, it flows back to the oil tank 130 through the fourth oil pipe 315. At this point, the hydraulic oil in the oil tank 130 flows into the rod chamber of the first loading cylinder 300 through the fifth oil pipe 316.

[0076] Similarly, when the first hydraulic control circuit 110 drives the telescopic rod of the tested hydraulic cylinder 100 to retract, the first loading cylinder 300 is extended by the pull of the tested hydraulic cylinder 100, opening the second stop valve 311 of the rodless chamber oil port of the first loading cylinder 300 and the second stop valve 311 of the rod chamber oil port of the first loading cylinder 300, and the hydraulic oil flows back to the oil tank 130 through the third oil pipe 314. At this time, the hydraulic oil in the oil tank 130 flows into the rodless chamber of the first loading cylinder 300 through the sixth oil pipe 317.

[0077] By simultaneously closing the second shutoff valve 311 of the rodless chamber oil port of the first loading cylinder 300 and the second shutoff valve 311 of the rod chamber oil port of the first loading cylinder 300, the telescopic position of the tested hydraulic cylinder 100 can be locked. By adjusting the opening pressure of the first relief valve 312 and the second relief valve 313, the load of the tested hydraulic cylinder 100 can be adjusted.

[0078] Regarding the third hydraulic control circuit 210 of the present invention, the third hydraulic control circuit 210 includes a second hydraulic pump 211, a second reversing valve 212, a first speed regulating valve 213, a second speed regulating valve 214, and a third relief valve 215. The second hydraulic pump 211 is connected to the oil inlet of the second reversing valve 212. The third oil outlet of the second reversing valve 212 is connected to the rodless chamber of the second loading cylinder 200 via the first speed regulating valve 213. The fourth oil outlet of the second reversing valve 212 is connected to the rod chamber of the second loading cylinder 200 via the second speed regulating valve 214.

[0079] A third overflow valve 215 is provided on the oil inlet of the second hydraulic pump 211 and the second reversing valve 212. In other words, the oil inlet of the third overflow valve 215 is connected to the pipeline between the second hydraulic pump 211 and the second reversing valve 212, and the oil outlet of the third overflow valve 215 is connected to the oil tank 130 of the hydraulic cylinder working condition simulation test control system.

[0080] The third relief valve 215 is used to regulate the system pressure, the first speed regulating valve 213 is used to adjust the extension speed of the second loading cylinder 200, and the second speed regulating valve 214 is used to adjust the retraction speed of the second loading cylinder 200. The second reversing valve 212 can be a three-position, four-way solenoid reversing valve, which is used to control the extension and retraction of the second loading cylinder 200, that is, the direction of force application.

[0081] like Figure 3 As shown, for example, the dynamic load output by the second loading cylinder 200 can be in other forms such as constant loading, unidirectional pulsating loading, or bidirectional sinusoidal loading. That is, the radial loading force variation curve of the second loading cylinder 200 can be a constant loading line, a unidirectional pulsating loading line, a bidirectional sinusoidal loading line, or other linear lines.

[0082] When the second loading cylinder 200 applies a constant load to the hydraulic cylinder 100 under test, the opening pressure of the third relief valve 215 is set to F1. After the second reversing valve 212 is switched, the telescopic rod of the second loading cylinder 200 retracts, and the telescopic rod of the hydraulic cylinder 100 under test is raised. When the pressure in the third hydraulic control circuit 210 reaches the preset opening pressure F1 of the third relief valve 215, the second loading cylinder 200 remains stationary until the test time is met. Of course, the telescopic rod of the second loading cylinder 200 can also be extended to press the telescopic rod of the hydraulic cylinder 100 under test.

[0083] When the second loading cylinder 200 applies a unidirectional pulsating load to the tested hydraulic cylinder 100, the telescopic rod of the tested hydraulic cylinder 100 initially coincides with the axis of the first telescopic rod 301. By setting the opening pressure of the third relief valve 215 to F2, the flow rates of the hydraulic oil flowing through the first and second speed regulating valves 213 and 214 are adjusted, thereby controlling the extension and retraction speeds of the second loading cylinder 200, which can be either consistent or inconsistent.

[0084] After the second reversing valve 212 switches direction, the second telescopic rod 201 rapidly retracts, rapidly raising the telescopic rod of the hydraulic cylinder 100 under test. When the pressure in the third hydraulic control circuit 210 reaches the preset opening pressure F2 of the third relief valve 215, the second loading cylinder 200 remains stationary until the test time expires. The second reversing valve 212 switches direction again, and the second telescopic rod 201 rapidly returns to its original position. This completes one unidirectional pulsation cycle, and the above sequence is repeated a predetermined number of times.

[0085] When the second loading cylinder 200 applies a bidirectional sinusoidal load to the tested hydraulic cylinder 100, the preset opening pressure F3 of the third relief valve 215 is preset, and the flow rate of the hydraulic oil flowing through the first speed control valve 213 and the second speed control valve 214 is adjusted to control the extension and retraction speeds of the second loading cylinder 200, which can be consistent or inconsistent. The third relief valve 215 can be an electromagnetic relief valve, and the curve of the control voltage input can be controlled to continuously control the change of the control pressure of the electromagnetic relief valve.

[0086] After the second reversing valve 212 is switched, the second telescopic rod 201 gradually retracts based on the changes in the control pressure of the electromagnetic relief valve, gradually raising the telescopic rod of the tested hydraulic cylinder 100. When the pressure in the third hydraulic control circuit 210 reaches the preset maximum opening pressure F3 of the electromagnetic relief valve, the second reversing valve 212 is switched, and the second telescopic rod 201 gradually extends based on the changes in the control pressure of the electromagnetic relief valve. After passing the initial position of the second telescopic rod 201, it continues to retract. The telescopic rod of the tested hydraulic cylinder 100 is gradually depressed. When the pressure in the third hydraulic control circuit 210 again reaches the preset maximum opening pressure F3 of the electromagnetic relief valve, the second reversing valve 212 is switched again, and the second loading cylinder 200 returns to its original position. This completes a bidirectional sinusoidal process, which is repeated a predetermined number of times. The changes in the sinusoidal curve applied to the second telescopic rod 201 are obtained by controlling the voltage curve of the electromagnetic reversing valve.

[0087] like Figure 4 As shown, the present invention also provides a hydraulic cylinder working condition simulation test method, comprising the following steps:

[0088] S1 : Setting the axial loading force of the first loading cylinder 300 ; that is, adjusting the opening pressures of the first relief valve 312 and the second relief valve 313 in the second hydraulic control circuit 310 .

[0089] S2: Based on the performance requirements of the tested hydraulic cylinder 100, select the loading force variation curve; for example, when testing the anti-eccentric load capacity of a general hydraulic cylinder, you can select Figure 3 For crane outrigger cylinders, you can select Figure 3 One-way pulsating loading line in; for pumping outrigger cylinders, you can choose Figure 3 Bidirectional sinusoidal loading line in .

[0090] S3: Based on the selected loading force variation curve, the action of the radially loaded second loading cylinder 200 is controlled; that is, the second loading cylinder 200 is controlled by the third hydraulic control circuit 210 to realize the loading force parameters of the selected loading force variation curve to dynamically load the tested hydraulic cylinder 100.

[0091] S4: Supply oil to the first chamber of the tested hydraulic cylinder 100. Specifically, the first chamber can be either the rod chamber or the rodless chamber of the tested hydraulic cylinder 100, and the second chamber can be the other of the two chambers. For example, if the first chamber is the rodless chamber, oil is supplied to the rodless chamber via the first hydraulic control circuit 110, and the first shutoff valve 114 of the first oil pipe is closed.

[0092] S5: Obtain the oil leakage from the second chamber of the tested hydraulic cylinder 100 to determine the internal leakage. For example, if the second chamber is the rod chamber, remove the quick-connect connector 113 in the first hydraulic control circuit 110 that connects to the rod chamber of the tested hydraulic cylinder 100 and open the first shutoff valve 114 of the second oil pipe. The oil leakage from the rod chamber is introduced into the weighing assembly 120 to calculate the internal leakage.

[0093] refer to Figure 5 In another embodiment of the present invention, before the step of setting the axial loading force of the first loading cylinder 300, the hydraulic cylinder working condition simulation test method further includes the following steps for measuring the initial internal leakage of the tested hydraulic cylinder 100:

[0094] S11 : Locking the tested hydraulic cylinder 100 ; in other words, closing the second stop valve 311 of the rod chamber and rodless chamber oil ports of the first loading cylinder 300 .

[0095] S12: Supply oil to the first chamber of the tested hydraulic cylinder 100. Specifically, the first chamber can be one of the rod chamber and the rodless chamber of the tested hydraulic cylinder 100, and the second chamber can be the other of the two. For example, if the first chamber is the rodless chamber, oil is supplied to the rodless chamber via the first hydraulic control circuit 110, and the first shut-off valve 114 of the first oil pipe is closed.

[0096] S13: Obtain the leaked oil from the second chamber of the tested hydraulic cylinder 100 to determine the initial internal leakage. For example, if the second chamber is the rod chamber, remove the quick-connect connector 113 in the first hydraulic control circuit 110 that connects to the rod chamber of the tested hydraulic cylinder 100 and open the first shut-off valve 114 of the second oil pipe. The leaked oil from the rod chamber is introduced into the weighing assembly 120 to calculate the initial internal leakage. This verifies whether the tested hydraulic cylinder 100 meets factory standards in its initial state.

[0097] Before introducing the leaked oil from the rod chamber into weighing assembly 120, drain the remaining oil from the pipe naturally. For example, allow the hydraulic oil in the second oil pipe to drain naturally, ensuring no continuous dripping for a period of time, such as 1 minute. Then, connect the second oil pipe to weighing assembly 120, maintain oil supply to the first chamber for a period of time, such as 5 minutes, then stop adding oil and calculate the initial internal leakage.

[0098] In addition, in some embodiments of the present invention, continue to refer to Figure 5 Before measuring the initial internal leakage of the tested hydraulic cylinder 100, the process further includes step S10: fully exhausting the tested hydraulic cylinder 100. Specifically, after the tested hydraulic cylinder 100 is connected to the first hydraulic control circuit 110 via the quick-connect connector 113, the first hydraulic control circuit 110 drives the tested hydraulic cylinder 100 to perform a circular reciprocating motion several times to fully exhaust the air in the tested hydraulic cylinder 100 and the first hydraulic control circuit 110.

[0099] The hydraulic cylinder working condition simulation test device provided by the present invention simulates the working condition of the hydraulic cylinder 100 being tested under different loads by arranging a first loading cylinder 300 in the axial direction of the hydraulic cylinder 100 being tested, and simulates the working condition of the hydraulic cylinder 100 being tested under different loads by arranging a second loading cylinder 200 in the radial direction of the hydraulic cylinder 100 being tested, so as to simulate the working condition of the hydraulic cylinder 100 being tested and not being coaxial with the load it is subjected to, that is, testing the anti-eccentric load capability; the second loading cylinder 200 can simulate the situation where the hydraulic cylinder 100 being tested is subjected to dynamic radial load, thereby meeting various performance tests of hydraulic cylinders with different needs, and has a wide range of applications.

[0100] Furthermore, in the hydraulic cylinder working condition simulation test control system provided by the present invention, since it has the hydraulic cylinder working condition simulation test device as described above, it also has the various advantages as described above. The hydraulic cylinder working condition simulation test method is a control method corresponding to the hydraulic cylinder working condition simulation test device, and therefore also has the advantages of the hydraulic cylinder working condition simulation test device.

[0101] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the various embodiments of the present invention.

Claims

1. A hydraulic cylinder working condition simulation test device, characterized in that: include: a first loading cylinder, wherein a first telescopic rod of the first loading cylinder is connected to the telescopic rod of the hydraulic cylinder under test, and the axis of the first telescopic rod coincides with the axis of the telescopic rod of the hydraulic cylinder under test; and a second hydraulic control circuit is used to control the load applied by the first loading cylinder to the hydraulic cylinder under test; a second loading cylinder, wherein a second telescopic rod of the second loading cylinder is used to connect with the telescopic rod of the tested hydraulic cylinder, and in an initial state, the second telescopic rod is perpendicular to the axis of the telescopic rod of the tested hydraulic cylinder; Wherein, the second loading cylinder is used to apply a dynamic load to the telescopic rod of the tested hydraulic cylinder; The third hydraulic control circuit is connected to the second loading cylinder. The third hydraulic control circuit includes a second hydraulic pump, a second reversing valve, a first speed regulating valve, a second speed regulating valve and a third overflow valve. The second hydraulic pump is connected to the oil inlet of the second reversing valve, the third oil outlet of the second reversing valve is connected to the rodless chamber of the second loading cylinder through the first speed regulating valve, the fourth oil outlet of the second reversing valve is connected to the rod chamber of the second loading cylinder through the second speed regulating valve, the oil inlet of the third overflow valve is connected to the pipeline between the second hydraulic pump and the second reversing valve, the oil outlet of the third overflow valve is connected to the oil tank of the hydraulic cylinder working condition simulation test control system, the third overflow valve is used to adjust the system pressure, the first speed regulating valve is used to adjust the extension speed of the second loading cylinder, and the second speed regulating valve is used to adjust the retraction speed of the second loading cylinder.

2. The hydraulic cylinder working condition simulation test device according to claim 1, characterized in that: It also includes a box body and a movable frame, wherein the movable frame is arranged on the box body and can be displaced on the box body; One side of the box is connected to the tested hydraulic cylinder, and the other side of the box is connected to the first loading cylinder. The telescopic rod of the tested hydraulic cylinder and the first telescopic rod are placed in the box; The cylinder body of the second loading cylinder is installed on the moving frame.

3. The hydraulic cylinder working condition simulation test device according to claim 1 or 2, characterized in that: It also includes an articulated shaft, the telescopic rod of the tested hydraulic cylinder and the second telescopic rod are hinged to one end of the articulated shaft, and the first telescopic rod is hinged to the other end of the articulated shaft.

4. A hydraulic cylinder working condition simulation test control system, characterized in that: A hydraulic cylinder operating condition simulation test device comprising a first hydraulic control circuit, a second hydraulic control circuit, a third hydraulic control circuit, and any one of claims 1 to 3; Wherein, the first hydraulic control circuit is connected to the tested hydraulic cylinder, the second hydraulic control circuit is connected to the first loading cylinder, and the third hydraulic control circuit is connected to the second loading cylinder.

5. The hydraulic cylinder working condition simulation test control system according to claim 4, characterized in that: The first hydraulic control circuit includes a first hydraulic pump and a first reversing valve, wherein the first hydraulic pump is connected to the first reversing valve; Wherein, a quick-connect connector is provided between the first reversing valve and the oil ports of the rod chamber and the rodless chamber of the hydraulic cylinder to be tested.

6. The hydraulic cylinder working condition simulation test control system according to claim 5, characterized in that: It also includes a weighing assembly and an oil pipe, one end of the oil pipe is arranged between the tested hydraulic cylinder and the quick-connect connector, and the other end of the oil pipe is connected to the weighing assembly; Wherein, the oil pipe is provided with a first stop valve.

7. The hydraulic cylinder working condition simulation test control system according to any one of claims 4 to 6, characterized in that: The second hydraulic control circuit includes a second shut-off valve, and the second shut-off valve is provided between the first loading cylinder and the oil tank of the hydraulic cylinder working condition simulation test control system.

8. The hydraulic cylinder working condition simulation test control system according to claim 7, characterized in that: The second hydraulic control circuit further includes a relief valve, which is disposed between the oil tank and the second cut-off valve.

9. A hydraulic cylinder working condition simulation test method, characterized in that: include: Setting the axial loading force of the first loading cylinder; Select the loading force variation curve based on the performance requirements of the hydraulic cylinder being tested; Based on the selected loading force variation curve, controlling the action of the second loading cylinder for radial loading; supplying oil to the first chamber of the tested hydraulic cylinder; Obtaining the leakage oil of the second chamber of the tested hydraulic cylinder to obtain the internal leakage amount; The second hydraulic control circuit is used to control the load of the first loading cylinder on the tested hydraulic cylinder; The third hydraulic control circuit is connected to the second loading cylinder. The third hydraulic control circuit includes a second hydraulic pump, a second reversing valve, a first speed regulating valve, a second speed regulating valve and a third overflow valve. The second hydraulic pump is connected to the oil inlet of the second reversing valve, the third oil outlet of the second reversing valve is connected to the rodless chamber of the second loading cylinder through the first speed regulating valve, the fourth oil outlet of the second reversing valve is connected to the rod chamber of the second loading cylinder through the second speed regulating valve, the oil inlet of the third overflow valve is connected to the pipeline between the second hydraulic pump and the second reversing valve, the oil outlet of the third overflow valve is connected to the oil tank of the hydraulic cylinder working condition simulation test control system, the third overflow valve is used to adjust the system pressure, the first speed regulating valve is used to adjust the extension speed of the second loading cylinder, and the second speed regulating valve is used to adjust the retraction speed of the second loading cylinder.

10. The hydraulic cylinder working condition simulation test method according to claim 9, characterized in that: Before setting the axial loading force of the first loading cylinder, the method further includes: Lock the hydraulic cylinder under test; supplying oil to the first chamber of the tested hydraulic cylinder; The leaked oil of the second chamber of the tested hydraulic cylinder is obtained to obtain an initial internal leakage amount.

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