CN114278649A - Hydraulic cylinder working condition simulation test device, control system and method - Google Patents
Hydraulic cylinder working condition simulation test device, control system and method Download PDFInfo
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- CN114278649A CN114278649A CN202210109335.1A CN202210109335A CN114278649A CN 114278649 A CN114278649 A CN 114278649A CN 202210109335 A CN202210109335 A CN 202210109335A CN 114278649 A CN114278649 A CN 114278649A
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Abstract
The invention relates to the field of hydraulic cylinder performance test, and provides a hydraulic cylinder working condition simulation test device, a control system and a method thereof, wherein the hydraulic cylinder working condition simulation test device comprises: the first loading cylinder is connected with the tested hydraulic cylinder, and the axes of the first loading cylinder and the second loading cylinder are overlapped; the second loading cylinder is connected with the tested hydraulic cylinder, and the axis of the second loading cylinder is vertical to the tested hydraulic cylinder; the second loading cylinder is capable of applying a dynamic load to the tested hydraulic cylinder. The defect that dynamic unbalance loading cannot be radially applied to the hydraulic cylinder and the unbalance loading resistance performance test cannot be carried out in the prior art is overcome. According to the hydraulic cylinder working condition simulation test device provided by the invention, the second loading cylinder is radially arranged on the tested hydraulic cylinder to test the unbalance loading resistance; the second loading cylinder can simulate the condition that the tested hydraulic cylinder is subjected to dynamic radial load, so that various performance tests of hydraulic cylinders with different requirements are met, and the application range is wide.
Description
Technical Field
The invention relates to the technical field of hydraulic cylinder performance testing, in particular to a hydraulic cylinder working condition simulation test device, a control system and a method thereof.
Background
At present, the hydraulic cylinder mostly carries out 9 test items such as test operation, starting pressure characteristic test, pressure resistance test and the like according to GB/T15622-2005 hydraulic cylinder test method, and does not contain an unbalance loading working condition simulation test item. After fault parts such as a pump truck support oil cylinder, a crane support oil cylinder, an excavator bucket oil cylinder and the like are analyzed, the fact that the working condition that the installation position of the oil cylinder is not coaxial with the load running track is very common in the actual working condition is found. The unbalance loading condition is one of the key factors of many faults such as internal leakage, external leakage, piston rod fracture, cylinder inner wall pull and the like of the oil cylinder. Especially for the supporting leg oil cylinder of a pump truck, when the main engine continuously pumps materials, the large impact generated at the moment of reversing is enough to cause the supporting leg oil cylinder to generate a periodic unbalance loading working condition. Once the oil cylinder has internal leakage or external leakage, the safety events such as the rollover of the whole machine and the like are easily caused. Therefore, a condition simulation test for the unbalance loading resistance of the hydraulic cylinder is necessary and meaningful.
The existing hydraulic cylinder working condition simulation test device cannot radially apply dynamic unbalance loading to the hydraulic cylinder to test the unbalance loading resistance performance.
Disclosure of Invention
The invention provides a hydraulic cylinder working condition simulation test device, a control system and a method thereof, which are used for solving the defect that the prior art can not radially apply dynamic unbalance loading to a hydraulic cylinder to perform an unbalance loading resistance test.
The invention provides a hydraulic cylinder working condition simulation test device, which comprises:
the first telescopic rod of the first loading cylinder is used for being connected with the telescopic rod of the tested hydraulic cylinder, and the axis of the first telescopic rod is superposed with that of the telescopic rod of the tested hydraulic cylinder;
the second telescopic rod of the second loading cylinder is used for being connected 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;
and the second loading cylinder is used for applying dynamic load to the telescopic rod of the tested hydraulic cylinder.
The hydraulic cylinder working condition simulation test device provided by the invention further comprises a box body and a moving frame, wherein the moving frame is arranged on the box body and can move on the box body;
one side of the box body is connected with the tested hydraulic cylinder, the other side of the box body is connected with the first loading cylinder, and a telescopic rod of the tested hydraulic cylinder and the first telescopic rod are arranged in the box body;
and the cylinder body of the second loading cylinder is arranged on the movable frame.
The hydraulic cylinder working condition simulation test device provided by the invention further comprises a hinge shaft, the telescopic rod and the second telescopic rod of the tested hydraulic cylinder are hinged with one end of the hinge shaft, and the first telescopic rod is hinged with the other end of the hinge shaft.
The invention also provides a hydraulic cylinder working condition simulation test control system, which comprises a first hydraulic control loop, a second hydraulic control loop, a third hydraulic control loop and the hydraulic cylinder working condition simulation test device;
the first hydraulic control circuit is connected with the tested hydraulic cylinder, the second hydraulic control circuit is connected with the first loading cylinder, and the third hydraulic control circuit is connected with the second loading cylinder.
According to the hydraulic cylinder working condition simulation test control system provided by the invention, the first hydraulic control loop comprises a first hydraulic pump and a first reversing valve, and the first hydraulic pump is connected with the first reversing valve;
and a quick connector is arranged between the first reversing valve and an oil port of a rod cavity and a rodless cavity of the tested hydraulic cylinder.
The hydraulic cylinder working condition simulation test control system further comprises a weighing component and an oil pipe, wherein one end of the oil pipe is arranged between the tested hydraulic cylinder and the quick-connection connector, and the other end of the oil pipe is communicated with the weighing component;
wherein the oil pipe is provided with a first shut-off valve.
According to the hydraulic cylinder working condition simulation test control system provided by the invention, the second hydraulic control loop comprises a second stop valve, and the second stop valve is arranged between the first loading cylinder and an oil tank of the hydraulic cylinder working condition simulation test control system.
According to the hydraulic cylinder working condition simulation test control system provided by the invention, the second hydraulic control loop further comprises an overflow valve, and the overflow valve is arranged between the oil tank and the second stop valve.
The invention also provides a hydraulic cylinder working condition simulation test method, which comprises the following steps:
setting the axial loading force of the first loading cylinder;
selecting a loading force change curve based on the performance requirement of the tested hydraulic cylinder;
controlling the action of a second loading cylinder for radial loading based on the selected loading force variation curve;
supplying oil to the first chamber of the tested hydraulic cylinder;
and obtaining the leakage oil of the second cavity of the tested hydraulic cylinder to obtain the internal leakage.
According to the hydraulic cylinder working condition simulation test method provided by the invention, before the setting of the axial loading force of the first loading cylinder, the method further comprises the following steps:
locking the tested hydraulic cylinder;
supplying oil to the first chamber of the tested hydraulic cylinder;
and obtaining the leakage oil of the second cavity of the tested hydraulic cylinder to obtain the initial internal leakage.
The hydraulic cylinder working condition simulation test device provided by the invention simulates the working conditions of different loads on the tested hydraulic cylinder by arranging the first loading cylinder in the axial direction of the tested hydraulic cylinder, and simulates the working conditions of different axes of the tested hydraulic cylinder and the loads, namely the eccentric load resistance of the test by arranging the second loading cylinder in the radial direction of the tested hydraulic cylinder; the second loading cylinder can simulate the condition that the tested hydraulic cylinder is subjected to dynamic radial load, so that various performance tests of hydraulic cylinders with different requirements are met, and the application range is wide.
Further, in the hydraulic cylinder working condition simulation test control system provided by the invention, the hydraulic cylinder working condition simulation test device is provided, so that the hydraulic cylinder working condition simulation test control system also has various advantages as described above, and the hydraulic cylinder working condition simulation test method is a control method corresponding to the hydraulic cylinder working condition simulation test device, so that the hydraulic cylinder working condition simulation test control system also has the advantages of the hydraulic cylinder working condition simulation test device.
Drawings
In order to more clearly illustrate the technical solutions of the present invention or the prior art, the drawings needed for the description of the embodiments or the prior art will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and those skilled in the art can also obtain other drawings according to the drawings without creative efforts.
FIG. 1 is a schematic structural diagram of a hydraulic cylinder working condition simulation test device provided by the invention;
FIG. 2 is a schematic diagram of a hydraulic cylinder condition simulation test control system provided by the present invention;
FIG. 3 is a graph illustrating the variation of the loading force of the dynamic load of the second loading cylinder provided by the present invention;
FIG. 4 is a flow chart of a hydraulic cylinder condition simulation test method provided by the present invention;
FIG. 5 is a second flowchart of the hydraulic cylinder working condition simulation test method provided by the present invention.
Reference numerals:
100: a tested hydraulic cylinder; 110: a first hydraulic control circuit; 111: a first hydraulic pump; 112: a first direction changing valve; 113: a quick connector; 114: a first shut-off valve; 120: a weighing assembly; 130: an oil tank;
200: a second loading cylinder; 201: a second telescopic rod; 210: a third hydraulic control circuit; 211: a second hydraulic pump; 212: a second directional control valve; 213: a first speed regulating valve; 214: a second speed regulating valve; 215: a third overflow valve;
300: a first loading cylinder; 301: a first telescopic rod; 310: a second hydraulic control loop; 311: a second stop valve; 312: a first overflow valve; 313: a second overflow valve; 314: a third oil pipe; 315: a fourth oil pipe; 316: a fifth oil pipe; 317: a sixth oil pipe;
400: a box body; 401: a movable frame; 402: and (4) hinging the shaft.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention clearer, the technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the description of the embodiments of the present invention, it should be noted that the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of describing the embodiments of the present invention and simplifying the description, but do not indicate or imply that the referred devices or elements must have a specific orientation, be configured in a specific orientation, and operate, and thus, should not be construed as limiting the embodiments of the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the embodiments of the present invention, it should be noted that, unless explicitly stated or limited otherwise, the terms "connected" and "connected" are to be interpreted broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; may be directly connected or indirectly connected through an intermediate. Specific meanings of the above terms in the embodiments of the present invention can be understood in specific cases by those of ordinary skill in the art.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of an embodiment of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.
Embodiments of the present invention will be described below with reference to fig. 1 to 5. It is to be understood that the following description is only exemplary embodiments of the present invention and is not intended to limit the present invention.
As shown in fig. 1, the present invention provides a hydraulic cylinder working condition simulation test apparatus, which includes: a first loading cylinder 300 applying an axial force to the tested hydraulic cylinder 100, and a second loading cylinder 200 applying a radial force to the tested hydraulic cylinder 100.
Specifically, the first telescopic rod 301 of the first loading cylinder 300 is used for being connected with the telescopic rod of the tested hydraulic cylinder 100, and the first telescopic rod 301 is overlapped with the telescopic rod axis of the tested hydraulic cylinder 100; the second telescopic rod 201 of the second loading cylinder 200 is used for being connected with the telescopic rod of the tested hydraulic cylinder 100, and in an initial state, the second telescopic rod 201 is perpendicular to the telescopic rod axis of the tested hydraulic cylinder 100; the second loading cylinder 200 is used for applying a dynamic load to the telescopic rod of the tested hydraulic cylinder 100.
The axial force applied by the first loading cylinder 300 corresponds to the load of the tested hydraulic cylinder 100, and the radial force applied by the second loading cylinder 200 corresponds to the offset load applied to the tested hydraulic cylinder 100 in the working state. In other words, the second loading cylinder 200 applies a radial force to the tested hydraulic cylinder 100, which corresponds to a working condition that the tested hydraulic cylinder 100 is not coaxial with the load operation track. The dynamic load provided by the second loading cylinder 200 may be a constant loading force after a certain loading, a loading force with a unidirectional pulsation trend, or a loading force with a bidirectional sine trend.
For example, in a first operating condition: in the process of extending or retracting the telescopic rod of the tested hydraulic cylinder 100, the internal leakage of the tested hydraulic cylinder 100 at the specified position can be measured by controlling the plugging of the oil ports of the rod cavity and the rodless cavity of the first loading cylinder 300, namely the internal leakage of the tested hydraulic cylinder 100 under the opposite pressure maintaining working condition.
Under a second working condition: the oil ports of the rod cavity and the rodless cavity of the first loading cylinder 300 are sealed, radial dynamic loads are applied through the second loading cylinder 200, and the internal leakage of the two cavities of the tested hydraulic cylinder 100 is measured respectively.
Under a third working condition: setting the opening pressure to the oil return ports of the rod chamber and the rodless chamber of the first loading cylinder 300 applies a certain load to the tested hydraulic cylinder 100 through the first loading cylinder 300. The tested hydraulic cylinder 100 performs the stretching action, and after the accumulated stretching action of the tested hydraulic cylinder 100 reaches the preset value, the internal leakage amount measurement of the opposite pressure maintaining is performed. For example, the cumulative number of times reaches 20 ten thousand or the cumulative trip reaches 100 kilometers. And then the measurement of the internal leakage amount of the top twitch is completed.
Under a fourth working condition: setting the opening pressure to the oil return ports of the rod chamber and the rodless chamber of the first loading cylinder 300 applies a certain load to the tested hydraulic cylinder 100 through the first loading cylinder 300. Meanwhile, the second loading cylinder 200 applies a dynamic load, and the hydraulic cylinder 100 under test expands and contracts while applying an axial load and a radial load. After the accumulated telescopic actions of the tested hydraulic cylinder 100 reach a preset value, the internal leakage amount of the opposite pressure maintaining is measured. For example, the cumulative number of times reaches 20 ten thousand or the cumulative trip reaches 100 kilometers. Namely, the measurement of the internal leakage amount of the top unbalance loading is completed.
With continued reference to fig. 1, in an embodiment of the present invention, the hydraulic cylinder working condition simulation test apparatus further includes a box 400 and a moving rack 401, wherein the moving rack 401 is disposed on the box 400, and the moving rack 401 is capable of moving on the box 400; one side of the box body 400 is connected with the tested hydraulic cylinder 100, the other side of the box body 400 is connected with the first loading cylinder 300, and the telescopic rod and the first telescopic rod 301 of the tested hydraulic cylinder 100 are arranged in the box body 400; the cylinder body of the second loading cylinder 200 is connected to the moving frame 401.
In other words, the case 400 includes an inner cavity, a sidewall, and an opened upper surface on which the moving frame 401 is disposed, for example, on which the moving frame 401 can move. The cylinder body of the tested hydraulic cylinder 100 is connected with the side wall, the cylinder body of the first loading cylinder 300 is connected with the side wall, the first loading cylinder 300 and the tested hydraulic cylinder 100 are oppositely arranged, and the cylinder body of the first loading cylinder 300 is fixedly connected with the side wall of the box body 400. The telescopic rod of the tested hydraulic cylinder 100 and the first telescopic rod 301 are arranged in the inner cavity, and the linear movement of the telescopic rod of the tested hydraulic cylinder 100 can drive the linear movement of the first telescopic rod 301. In the test state, the movement amounts of the first telescopic rod 301 and the second telescopic rod 201 are small.
The cylinder body of the second loading cylinder 200 is connected with the moving frame 401, the second telescopic rod 201 is connected with the telescopic rod of the tested hydraulic cylinder 100, and the moving frame 401 can be locked at a designated position on the upper surface of the box body 400. For example, in the process that the telescopic rod of the tested hydraulic cylinder 100 drives the first telescopic rod 301 to move, the moving frame 401 drives the second loading cylinder 200 to move along the axial direction of the telescopic rod of the tested hydraulic cylinder 100 and the first telescopic rod 301 without applying a loading force to the second loading cylinder 200. It is possible to realize the test mode of the roof whip without disassembling the second loading cylinder 200. The second loading cylinder 200 can adjust the angle of the radial loading force to the telescopic rod of the tested hydraulic cylinder 100.
The box 400 has a good safety protection function, and when the tested hydraulic cylinder 100 fails or a hydraulic element fails, the box 400 can play a good protection role. In the initial state, the axis of the second loading cylinder 200 coincides with the central axis of the moving frame 401.
For another example, the position of the movable frame 401 on the upper surface of the casing 400 may be adjusted by bolts, the cylinder body of the second loading cylinder 200 may be coupled to the movable frame 401 by a trunnion, and the second loading cylinder 200 may oscillate to a small extent when the hydraulic cylinder 100 to be tested reciprocates. The swing amplitude is mainly limited by the magnitude of the loading force of the first loading cylinder; of course, the clearance between the telescopic rod and the guide sleeve of the tested hydraulic cylinder and the clearance between the cylinder barrel and the piston. A swing with a swing angle of 30 degrees or less is generally considered to be a small-amplitude swing.
Further, in another embodiment of the present invention, the hydraulic cylinder working condition simulation test device further includes a hinge shaft 402, the telescopic rod and the second telescopic rod 201 of the tested hydraulic cylinder 100 are hinged to one end of the hinge shaft 402, and the first telescopic rod 301 is hinged to the other end of the hinge shaft 402. In other words, the first telescopic rod 301 is connected to the telescopic rod of the tested hydraulic cylinder 100 through the hinge shaft 402, and the radial loading force of the second telescopic rod 201 directly acts on the telescopic rod of the tested hydraulic cylinder 100. Therefore, when the second telescopic rod 201 applies radial loading force, the first telescopic rod 301 is prevented from deforming under stress or causing failure of the cylinder body, and the constancy of the loading force cannot be ensured.
As shown in fig. 2, the present invention further provides a hydraulic cylinder working condition simulation test control system, which includes 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 apparatus of the above embodiment; 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 charging cylinder 300, and the third hydraulic control circuit 210 is connected to the second charging cylinder 200.
Specifically, the first hydraulic control circuit 110 is used to control the extension and contraction of the tested hydraulic cylinder 100, the second hydraulic control circuit 310 is used to control the load of the first loading cylinder 300 on the tested hydraulic cylinder 100, and the third hydraulic control circuit 210 is used to control the extension and contraction of the second loading cylinder 200. For example, the second hydraulic control circuit 310 drives the second telescopic rod 201 to extend, the second telescopic rod 201 applies radial pressure to the tested hydraulic cylinder 100, the second hydraulic control circuit 310 drives the second telescopic rod 201 to retract, and the second telescopic rod 201 applies radial tension to the tested hydraulic cylinder 100. The second hydraulic control circuit 310 and the third hydraulic control circuit 210 may be activated simultaneously or independently, in other words, the first loading cylinder 300 and the second loading cylinder 200 may apply force to the tested hydraulic cylinder 100 simultaneously or may apply force to the tested hydraulic cylinder 100 independently.
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 national standard GB/T15622-2005 hydraulic cylinder, namely a test operation, b start pressure characteristic test, c pressure test, d durability test, e leakage test, f buffer test, g load efficiency test, h high temperature test and i stroke detection.
With continued reference to FIG. 2, in an alternative embodiment of the present invention, the first hydraulic control circuit 110 includes a first hydraulic pump 111 and a first directional control valve 112, the first hydraulic pump 111 being connected to the first directional control valve 112; wherein, a quick-connection plug 113 is arranged between the first reversing valve 112 and the rod cavity and the rodless cavity of the tested hydraulic cylinder 100. That is, the first hydraulic control circuit 110 is connected to the rod chamber and the rodless chamber of the tested hydraulic cylinder 100 through the quick connector 113, so as to facilitate plugging and unplugging. The first direction valve 112 may be a three-position four-way electromagnetic direction valve or a three-position four-way manual direction valve, and the extension and retraction of the tested hydraulic cylinder 100 is realized by switching the first direction valve 112. Wherein, the quick-connection plug 113 with a rod cavity or without a rod cavity of the tested hydraulic cylinder 100 can be independently disconnected according to the test requirement.
In addition, in another optional embodiment of the present invention, the hydraulic cylinder working condition simulation test control system further includes a weighing component 120 and an oil pipe, one end of the oil pipe is disposed between the tested hydraulic cylinder 100 and the quick-connect plug 113, and the other end of the oil pipe is communicated with the weighing component 120; wherein the oil pipe is provided with a first shut-off valve 114.
Specifically, the first direction valve 112 includes a first oil outlet and a second oil outlet, the first oil outlet is connected to the rodless cavity of the tested hydraulic cylinder 100 through the quick connector 113, and the second oil outlet is connected to the rod cavity of the tested hydraulic cylinder 100 through the quick connector 113. A first oil pipe is connected between the rodless cavity and the quick-connection-peg 113, one end of the first oil pipe is communicated with the rodless cavity, and the other end of the first oil pipe is communicated with the weighing component 120; and a second oil pipe is connected between the rod cavity and the quick-connection-peg 113, one end of the second oil pipe is communicated with the rod cavity, and the other end of the second oil pipe is communicated with the weighing component 120. The first and second oil lines are each provided with a first shut-off valve 114.
For example, it is necessary to detect the internal leakage of the rod chamber of the tested hydraulic cylinder 100, pull out the quick connector 113 between the second oil outlet and the rod chamber, and open the first cut-off valve 114 on the second oil pipe. Similarly, it is necessary to detect the internal leakage of the rodless cavity of the tested hydraulic cylinder 100, pull out the quick connector 113 between the first oil outlet and the rodless cavity, and open the first stop valve 114 on the first oil pipe. The amount of oil flowing into the weighing assembly 120 is the internal leakage amount, wherein the weighing assembly 120 can be a container and an electronic scale, and can meet the measurement requirements of the leakage amount in different ranges; can be a measuring cup, and the inner leakage can be directly read; the flowmeter can be used, the internal leakage instantaneous value can be read, and the flowmeter is suitable for occasions with increased internal leakage amount; the metering oil cylinder can be used, the internal leakage can be effectively quantified, and the metering oil cylinder is suitable for occasions with increased internal leakage.
Of course, the first hydraulic control circuit 110 further includes a one-way throttle valve disposed between the quick-connect coupling 113 and the first direction valve 112.
Further, in other embodiments of the present invention, the second hydraulic control circuit 310 includes a second cut-off valve 311, and the second cut-off valve 311 is disposed between the first loading cylinder 300 and the oil tank 130 of the hydraulic cylinder operation condition simulation test control system.
Specifically, a second shut-off valve 311 is provided in a line between the rod chamber of the first charging cylinder 300 and the tank 130, and a second shut-off valve 311 is also provided in a line between the rod chamber of the first charging cylinder 300 and the tank 130. In other words, the second hydraulic control circuit 310 has no hydraulic pump, and the first charging cylinder 300 discharges oil and sucks oil from the first charging cylinder 300 by pumping pressure of the tested hydraulic cylinder 100. That is, the second hydraulic control circuit 310 is connected to the rod chamber and the rodless chamber of the first charging cylinder 300 through two second cutoff valves 311.
With continued reference to fig. 2, in a preferred embodiment of the present invention, the second hydraulic control circuit 310 further includes a relief valve disposed between the oil tank 130 and the second shut-off valve 311. The relief valve may be an electromagnetic relief valve.
In other words, one second cut-off valve 311 is provided at the port of the rod chamber of the first loading cylinder 300, a third oil line 314 is provided between the second cut-off valve 311 and the oil tank 130, and a first relief valve 312 is provided in the third oil line 314; similarly, another second stop valve 311 is provided at the port of the rodless chamber of the first loading cylinder 300, a fourth oil pipe 315 is provided between the stop valve and the oil tank 130, and a second relief valve 313 is provided in the fourth oil pipe 315. Further, a first check valve is provided in third oil pipe 314, the first check valve being provided between second stop valve 311 and first relief valve 312, the first check valve allowing only hydraulic oil to flow from the rod chamber into oil tank 130. A second check valve is provided in the fourth oil pipe 315, the second check valve being provided between the second stop valve 311 and the second relief valve 313, the second check valve allowing only the hydraulic oil to flow from the rod-less chamber into the oil tank 130.
Further, a fifth oil pipe 316 is arranged between the second stop valve 311 with the rod cavity oil port and the oil tank 130, and a third check valve is arranged on the fifth oil pipe 316 and only allows hydraulic oil to flow into the rod cavity from the oil tank 130; a sixth oil pipe 317 is provided between the second shut-off valve 311 of the rod-less chamber port and the oil tank 130, and a fourth check valve is provided on the sixth oil pipe 317, the fourth check valve allowing only the hydraulic oil to flow from the oil tank 130 into the rod-less chamber.
That is, when the first hydraulic control circuit 110 drives the extension rod of the tested hydraulic cylinder 100 to extend, the first loading cylinder 300 retracts under the pushing of the tested hydraulic cylinder 100, the second stop valve 311 of the rod chamber port of the first loading cylinder 300 and the second stop valve 311 of the rod chamber port of the first loading cylinder 300 are opened, and the hydraulic oil of the rod chamber of the first loading cylinder 300 flows back to the oil tank 130 through the second stop valve 311, the second check valve and the second overflow valve 313, i.e., flows back to the oil tank 130 through the fourth oil pipe 315. At this time, 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.
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 extends under the pulling of the tested hydraulic cylinder 100, the second stop valve 311 of the rod-free cavity port of the first loading cylinder 300 and the second stop valve 311 of the rod cavity port of the first loading cylinder 300 are opened, and the hydraulic oil flows back to the oil tank 130 from 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.
And the second stop valve 311 of the rodless cavity port of the first loading cylinder 300 and the second stop valve 311 of the rod cavity port of the first loading cylinder 300 are closed at the same time, so that the locking of the telescopic position of the tested hydraulic cylinder 100 can be realized. The opening pressures of the first overflow valve 312 and the second overflow valve 313 are adjusted, so that the load of the hydraulic cylinder 100 to be tested can be adjusted.
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 direction changing 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 with an oil inlet of a second directional valve 212, a third oil outlet of the second directional valve 212 is connected with a rodless cavity of the second loading cylinder 200 through a first speed regulating valve 213, and a fourth oil outlet of the second directional valve 212 is connected with a rod cavity of the second loading cylinder 200 through a second speed regulating valve 214.
The third overflow valve 215 is arranged at the oil inlets 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 with the oil tank 130 of the hydraulic cylinder working condition simulation test control system.
The third relief valve 215 is used to regulate the system pressure, the first speed valve 213 is used to regulate the extension speed of the second loading cylinder 200, and the second speed valve 214 is used to regulate the retraction speed of the second loading cylinder 200. The second directional valve 212 may be a three-position, four-way electromagnetic directional valve for controlling the extension and retraction, i.e., the force application direction, of the second loading cylinder 200.
As shown in fig. 3, for example, the dynamic load output by the second loading cylinder 200 may be constant loading, unidirectional pulsating loading, or bidirectional sinusoidal loading, among other forms. That is, the radial loading force variation curve of the second loading cylinder 200 may be a constant loading line, a unidirectional pulsating loading line or a bidirectional sinusoidal loading line, or other linearity.
When the second loading cylinder 200 applies a constant load to the tested hydraulic cylinder 100, the opening pressure of the third overflow valve 215 is set to be F1, after the second reversing valve 212 reverses, the telescopic rod of the second loading cylinder 200 retracts to lift the telescopic rod of the tested hydraulic cylinder 100, and when the pressure of the third hydraulic control circuit 210 reaches the preset opening pressure F1 of the third overflow valve 215, the second loading cylinder 200 remains still until the test time is met. Of course, the extension rod of the second loading cylinder 200 may also be extended to press down the extension rod of the tested hydraulic cylinder 100.
When the second loading cylinder 200 applies unidirectional pulsating loading to the tested hydraulic cylinder 100, the axis of the expansion link of the tested hydraulic cylinder 100 in the initial state coincides with the axis of the first expansion link 301. The opening pressure of the third spill valve 215 is set to F2, and the flow rate of the hydraulic oil flowing through the first speed valve 213 and the second speed valve 214 is adjusted to control the extension and retraction speeds of the second cylinder 200, which may or may not be uniform.
After the second reversing valve 212 is reversed, the second telescopic rod 201 retracts rapidly, the telescopic rod of the tested hydraulic cylinder 100 is lifted rapidly, and when the pressure of the third hydraulic control circuit 210 reaches the preset opening pressure F2 of the third overflow valve 215, the second loading cylinder 200 is kept still until the test time is met. The second reversing valve 212 reverses again and the second telescopic rod 201 returns to the original position quickly. And finishing a one-way pulsation process, and repeatedly performing the actions for a preset number of times.
When the second loading cylinder 200 applies the bidirectional sinusoidal loading 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 regulating valve 213 and the second speed regulating valve 214 is adjusted, so that the extending and retracting speeds of the second loading cylinder 200 are controlled, which may be uniform or nonuniform, and the third relief valve 215 may be an electromagnetic relief valve, which may control the continuous change of the control pressure of the electromagnetic relief valve by controlling the curve of the voltage input.
After the second reversing valve 212 is reversed, the second telescopic rod 201 retracts gradually based on the change of the control pressure of the electromagnetic overflow valve, the telescopic rod of the tested hydraulic cylinder 100 is lifted gradually, when the pressure of the third hydraulic control loop 210 reaches the preset maximum opening pressure F3 of the electromagnetic overflow valve, the second reversing valve 212 reverses, the second telescopic rod 201 extends gradually based on the change of the control pressure of the electromagnetic overflow valve, and the second telescopic rod 201 continues to stretch after passing through the initial position of the second telescopic rod 201. The telescopic rod of the tested hydraulic cylinder 100 is gradually pressed down, when the pressure of the third hydraulic control circuit 210 reaches the preset maximum opening pressure F3 of the electromagnetic overflow valve again, the second reversing valve 212 reverses again, and the second loading cylinder 200 returns to the original position. And finishing a bidirectional sine process, and repeating the actions for a preset number of times. The sinusoidal variation applied by the second telescopic rod 201 is obtained by controlling the voltage variation curve of the electromagnetic directional valve.
As shown in fig. 4, the invention also provides a hydraulic cylinder working condition simulation test method, which comprises the following steps:
s1: setting an axial loading force of the first loading cylinder 300; that is, the opening pressures of the first relief valve 312 and the second relief valve 313 in the second hydraulic control circuit 310 are adjusted.
S2: selecting a loading force variation curve based on the performance requirements of the tested hydraulic cylinder 100; for example: when the anti-unbalance loading capacity of a common hydraulic cylinder is tested, a constant loading line in the figure 3 can be selected; for the crane support leg oil cylinder, the unidirectional pulsation loading line in fig. 3 can be selected; for a pumping-type leg cylinder, the bidirectional sinusoidal loading line in fig. 3 may be selected.
S3: controlling the action of the second loading cylinder 200 for radial loading based on the selected loading force variation curve; that is, the third hydraulic control circuit 210 controls the second loading cylinder 200 to realize the selected loading force parameter of the loading force variation curve to dynamically load the tested hydraulic cylinder 100.
S4: supplying oil to the first chamber of the tested hydraulic cylinder 100; specifically, the first chamber may be one of a rod chamber and a rodless chamber of the hydraulic cylinder 100 under test, and the second chamber may be the other. For example, the first chamber is a rodless chamber, and the rodless chamber is supplied with oil through the first hydraulic control circuit 110, and the first cut valve 114 of the first oil pipe is closed.
S5: and (5) acquiring the leakage oil of the second cavity of the tested hydraulic cylinder 100 to obtain the internal leakage. For example, the second chamber is a rod chamber, the quick connector 113 at the end of the rod chamber of the tested hydraulic cylinder 100 in the first hydraulic control circuit 110 is pulled out, and the first stop valve 114 of the second oil pipe is opened. The leaking oil from the rod cavity is introduced into the weighing assembly 120 and the internal leakage is calculated.
Referring to fig. 5, in another embodiment of the present invention, prior to the step of setting the axial loading force of the first loading cylinder 300, the hydraulic cylinder operating condition simulation test method further includes the steps of:
s11: locking the tested hydraulic cylinder 100; in other words, the second shutoff valve 311 of the rod chamber and the rodless chamber ports of the first charging cylinder 300 is closed.
S12: supplying oil to the first chamber of the tested hydraulic cylinder 100; specifically, the first chamber may be one of a rod chamber and a rodless chamber of the hydraulic cylinder 100 under test, and the second chamber may be the other. For example, the first chamber is a rodless chamber, and the rodless chamber is supplied with oil through the first hydraulic control circuit 110, and the first cut valve 114 of the first oil pipe is closed.
S13: and acquiring the leakage oil of the second cavity of the tested hydraulic cylinder 100 to obtain the initial internal leakage. For example, the second chamber is a rod chamber, the quick connector 113 at the end of the rod chamber of the tested hydraulic cylinder 100 in the first hydraulic control circuit 110 is pulled out, and the first stop valve 114 of the second oil pipe is opened. The leaking oil from the rod cavity is introduced into the weigh assembly 120 and the initial internal leakage is calculated. That is, it is detected whether the initial state of the tested hydraulic cylinder 100 satisfies the factory standard.
Wherein the residual oil in the pipe is naturally drained before the leaked oil of the rod chamber is introduced into the weighing assembly 120. For example, the hydraulic oil in the second oil pipe is allowed to drain naturally, ensuring that no continuous oil dripping occurs for a period of time, for example, 1 minute. Then, the oil supply to the first chamber is maintained for a period of time, for example, 5 minutes, after the second oil pipe is connected to the weighing unit 120, the oil supply is stopped, and the initial internal leakage amount is calculated.
Further, in some embodiments of the present invention, with continued reference to fig. 5, before the initial internal leakage amount of the tested hydraulic cylinder 100 is measured, the method further includes step S10: the tested hydraulic cylinder 100 is sufficiently exhausted. Specifically, after the tested hydraulic cylinder 100 is connected to the first hydraulic control circuit 110 through the quick connector 113, the first hydraulic control circuit 110 drives the tested hydraulic cylinder 100 to perform reciprocating pumping for several times, so as to fully exhaust air in the tested hydraulic cylinder 100 and the first hydraulic control circuit 110.
According to the hydraulic cylinder working condition simulation test device provided by the invention, the working conditions of the tested hydraulic cylinder 100 under different loads are simulated by arranging the first loading cylinder 300 in the axial direction of the tested hydraulic cylinder 100, and the working conditions of the tested hydraulic cylinder 100 and the loads under different axes are simulated by arranging the second loading cylinder 200 in the radial direction of the tested hydraulic cylinder 100, namely the eccentric load resistance is tested; the second loading cylinder 200 can simulate the condition that the tested hydraulic cylinder 100 is subjected to dynamic radial load, so that various performance tests of hydraulic cylinders with different requirements are met, and the application range is wide.
Further, in the hydraulic cylinder working condition simulation test control system provided by the invention, the hydraulic cylinder working condition simulation test device is provided, so that the hydraulic cylinder working condition simulation test control system also has various advantages as described above, and the hydraulic cylinder working condition simulation test method is a control method corresponding to the hydraulic cylinder working condition simulation test device, so that the hydraulic cylinder working condition simulation test control system also has the advantages of the hydraulic cylinder working condition simulation test device.
Finally, it should be noted that: the above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions of the embodiments of the present invention.
Claims (10)
1. The utility model provides a pneumatic cylinder operating mode analogue test device which characterized in that includes:
the first telescopic rod of the first loading cylinder is used for being connected with the telescopic rod of the tested hydraulic cylinder, and the axis of the first telescopic rod is superposed with the axis of the telescopic rod of the tested hydraulic cylinder;
the second telescopic rod of the second loading cylinder is used for being connected 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;
and the second loading cylinder is used for applying dynamic load to the telescopic rod of the tested hydraulic cylinder.
2. The hydraulic cylinder working condition simulation test device according to claim 1, further comprising a box body and a movable frame, wherein the movable frame is arranged on the box body, and the movable frame can be displaced on the box body;
one side of the box body is connected with the tested hydraulic cylinder, the other side of the box body is connected with the first loading cylinder, and a telescopic rod of the tested hydraulic cylinder and the first telescopic rod are arranged in the box body;
and the cylinder body of the second loading cylinder is arranged on the movable frame.
3. The hydraulic cylinder working condition simulation test device according to claim 1 or 2, further comprising a hinge shaft, wherein the telescopic rod and the second telescopic rod of the hydraulic cylinder to be tested are hinged to one end of the hinge shaft, and the first telescopic rod is hinged to the other end of the hinge shaft.
4. A hydraulic cylinder working condition simulation test control system is characterized by comprising a first hydraulic control loop, a second hydraulic control loop, a third hydraulic control loop and a hydraulic cylinder working condition simulation test device as claimed in any one of claims 1 to 3;
the first hydraulic control circuit is connected with the tested hydraulic cylinder, the second hydraulic control circuit is connected with the first loading cylinder, and the third hydraulic control circuit is connected with the second loading cylinder.
5. The hydraulic cylinder working condition simulation test control system according to claim 4, wherein the first hydraulic control circuit comprises a first hydraulic pump and a first reversing valve, and the first hydraulic pump is connected with the first reversing valve;
and a quick connector is arranged between the first reversing valve and an oil port of a rod cavity and a rodless cavity of the tested hydraulic cylinder.
6. The hydraulic cylinder working condition simulation test control system according to claim 5, further comprising a weighing component and an oil pipe, wherein one end of the oil pipe is arranged between the tested hydraulic cylinder and the quick-connection connector, and the other end of the oil pipe is communicated with the weighing component;
wherein the oil pipe is provided with a first shut-off valve.
7. The hydraulic cylinder working condition simulation test control system according to any one of claims 4 to 6, wherein the second hydraulic control circuit comprises a second stop valve, and the second stop valve is arranged between the first loading cylinder and a 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, wherein the second hydraulic control circuit further comprises an overflow valve, and the overflow valve is arranged between the oil tank and the second stop valve.
9. A hydraulic cylinder working condition simulation test method is characterized by comprising the following steps:
setting the axial loading force of the first loading cylinder;
selecting a loading force change curve based on the performance requirement of the tested hydraulic cylinder;
controlling the action of a second loading cylinder for radial loading based on the selected loading force variation curve;
supplying oil to the first chamber of the tested hydraulic cylinder;
and obtaining the leakage oil of the second cavity of the tested hydraulic cylinder to obtain the internal leakage.
10. The hydraulic cylinder operating condition simulation test method according to claim 9, further comprising, before the setting the axial loading force of the first loading cylinder:
locking the tested hydraulic cylinder;
supplying oil to the first chamber of the tested hydraulic cylinder;
and obtaining the leakage oil of the second cavity of the tested hydraulic cylinder to obtain the initial internal leakage.
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117570087A (en) * | 2024-01-17 | 2024-02-20 | 浙江大学 | Bearing experiment method and experiment table for opposite-top cylinder |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117570087A (en) * | 2024-01-17 | 2024-02-20 | 浙江大学 | Bearing experiment method and experiment table for opposite-top cylinder |
| CN117570087B (en) * | 2024-01-17 | 2024-04-05 | 浙江大学 | Bearing experiment method and experiment table for opposite-top cylinder |
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