Oil cylinder synchronization and loading comprehensive experiment system under multiple loading conditions

Abstract

The utility model discloses an oil cylinder synchronization and loading comprehensive experiment system under multiple loading conditions, which relates to a hydraulic control system and comprises a plurality of groups of hydraulic cylinders arranged oppositely, and displacement sensors are mounted on telescopic rods of the hydraulic cylinders; each hydraulic cylinder is provided with a proportional direction valve group in a matched mode, a pressure oil port of each proportional direction valve group is connected with a hydraulic power source, an oil return port of each proportional direction valve group is connected with an oil tank, and two working oil ports of each proportional direction valve group are connected with a rodless cavity of the corresponding hydraulic cylinder and a rod cavity of the corresponding hydraulic cylinder respectively. And the proportional pressure-reducing overflow valve is arranged on the pressure-regulating oil way arranged on one group of hydraulic cylinders, pressure-reducing overflow valves are arranged on the pressure-regulating oil ways arranged on the other hydraulic cylinders, and rod cavities of the hydraulic cylinders are provided with unloading oil ways. According to the utility model, the control effects of different proportional valves under different load working conditions can be compared during an experiment.

Description

Technical Field

[0001] The utility model relates to a hydraulic control system, in particular to an oil cylinder synchronization and loading comprehensive experimental system under multiple loading conditions. Background Art

[0002] At present, the schemes of multi-cylinder synchronous control can be generally divided into three categories: mechanical synchronization, hydraulic synchronization, and electro-hydraulic proportional (servo) synchronization. In situations where the synchronization accuracy is required to be high, the electro-hydraulic proportional (servo) synchronization method is often used, but the control effect of the electro-hydraulic proportional (servo) synchronization system and the stability of the control system are related to many factors, such as: the type of hydraulic oil source, the type of proportional valve (servo valve), different load conditions, hydraulic oil temperature, control algorithm, etc. Due to the existence of these factors, when designing the electro-hydraulic proportional (servo) synchronization system, there are often certain difficulties in the selection of some components, the control range of some parameters, and the algorithm design.

[0003] At the same time, the current cylinder pressure control system solutions can be generally divided into: overflow valve pressure control, pressure reducing valve pressure control, pressure reducing overflow valve pressure control, proportional valve (servo valve) pressure control, switch valve pressure control, etc., and the pressure control effect and the stability of the control system are related to many factors, such as: different hydraulic oil sources, different types of control valves, different load conditions, hydraulic oil temperature, control algorithms, etc. Due to the existence of these factors, when designing an electro-hydraulic pressure control system, there are often certain difficulties in the selection of some components, the control range of some parameters, and the design of the algorithm.

[0004] In addition, in actual engineering design, due to tight project schedules and limited testing conditions, it is often impossible to conduct a more comprehensive test of the performance of the electro-hydraulic proportional (servo) synchronous control system and the electro-hydraulic pressure control system. The design of related test benches can solve this problem well.

[0005] At present, there is no hydraulic proportional (servo) synchronous control system that takes into account different types of proportional valves (servo valves) and different load conditions, and there is no hydraulic pressure control system that takes into account different types of control valves and different load conditions. Utility Model Content

[0006] The utility model aims to provide a comprehensive experimental system for oil cylinder synchronization and loading under multiple loading conditions, which can compare the control effects under different hydraulic oil sources, different proportional valves and different load conditions during the experiment.

[0007] In order to achieve the purpose of the utility model, the technical scheme adopted is: a comprehensive experimental system for cylinder synchronization and loading under multiple loading conditions, including hydraulic cylinders arranged relatively to each other, and the telescopic rods of the hydraulic cylinders are equipped with displacement sensors; it also includes a proportional directional valve group arranged in conjunction with the hydraulic cylinders, the pressure oil port of the proportional directional valve group is connected to the hydraulic power source, the return oil port of the proportional directional valve group is connected to the oil tank, and the two working oil ports of the proportional directional valve group are respectively connected to the rodless chamber of the hydraulic cylinder and the rod chamber of the hydraulic cylinder; a pressure regulating oil circuit is also connected between the hydraulic power source and the rodless chamber of the hydraulic cylinder, and a proportional pressure reducing overflow valve is installed on the pressure regulating oil circuit.

[0008] Furthermore, there are multiple groups of hydraulic cylinders arranged relatively to each other, and each hydraulic cylinder is equipped with a proportional directional valve group. The proportional pressure reducing overflow valve is installed on the pressure regulating oil circuit equipped with one group of hydraulic cylinders, and the pressure regulating oil circuits equipped with the remaining hydraulic cylinders are all equipped with pressure reducing overflow valves.

[0009] Furthermore, a unloading oil circuit is connected between the working oil port of the proportional directional valve group and the rod chamber of the hydraulic cylinder, and high-pressure stop valves are installed at the outlet end of the pressure reducing relief valve, the outlet end of the proportional pressure reducing relief valve, between the working oil port of the proportional directional valve group and the rodless chamber of the hydraulic cylinder, and on the unloading oil circuit.

[0010] Furthermore, pressure sensors are installed between the proportional pressure reducing relief valve and the rodless chamber of the hydraulic cylinder and on the oil outlet of the hydraulic power source.

[0011] Furthermore, pressure gauges are installed on the rodless chamber of the hydraulic cylinder and the oil outlet of the hydraulic power source.

[0012] The beneficial effects of the utility model are:

[0013] 1. When the utility model is used to experiment with a multi-cylinder synchronous control system, various load conditions can be simulated, especially conditions that are difficult to encounter during the actual equipment debugging process but may occur during the actual use of the equipment, so as to verify whether the proportional valve control cylinder system solution meets the design requirements and provide a reference for the optimal design of the hydraulic system.

[0014] 2. When the utility model is used to experiment with a multi-cylinder synchronous control system, the utility model can test a hydraulic system designed with different proportional valve-controlled cylinders, thereby testing the synchronization accuracy, positioning control accuracy, and speed of the hydraulic system of two proportional valve-controlled cylinders.

[0015] 3. When the utility model is used to experiment with a cylinder pressure control system, the utility model can test the influence on the pressure control effect of the proportional pressure control system under variable load conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] The accompanying drawings illustrate exemplary embodiments of the present invention and are used to explain the principles of the present invention together with the description. These drawings are included to provide a further understanding of the present invention, and the drawings are included in and constitute a part of this specification.

[0017] Figure 1 It is the hydraulic system diagram of the comprehensive experimental system of cylinder synchronization and loading under multiple loading conditions.

[0018] Markings and corresponding parts names in the attached drawings:

[0019] 16.1-16.4, proportional directional valve group 1, 17.1-17.24, high-pressure stop valve, 18.1-18.9, pressure gauge, 19.1-19.6, pressure reducing relief valve, 20.1, 20.2, proportional pressure reducing relief valve, 21.1-21.3, pressure sensor, 22.1-22.4, proportional directional valve group 2, 23.1-23.4, 26.1-26.4, displacement sensor, 24.1-24.4, hydraulic cylinder 1, 25.1-25.4, hydraulic cylinder 2, 26, main oil circuit, 28, pressure regulating oil circuit, 29, unloading oil circuit. DETAILED DESCRIPTION

[0020] The present invention is further described in detail below in conjunction with the accompanying drawings and implementations. It is to be understood that the specific implementations described herein are only used to explain the relevant content, rather than to limit the present invention. It should also be noted that, for ease of description, only the parts related to the present invention are shown in the accompanying drawings.

[0021] It should be noted that, in the absence of conflict, the embodiments and features of the embodiments of the present invention can be combined with each other. The present invention will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0022] like Figure 1As shown, the utility model provides a comprehensive experimental system for cylinder synchronization and loading under multiple loading conditions, including four groups of hydraulic cylinders, each group including hydraulic cylinder one and hydraulic cylinder two arranged relatively to each other, that is, the four hydraulic cylinders one in the present invention are hydraulic cylinder one 24.1, hydraulic cylinder one 24.2, hydraulic cylinder one 24.3, and hydraulic cylinder one 24.4, and the four hydraulic cylinders two are hydraulic cylinder two 25.1, hydraulic cylinder two 25.2, hydraulic cylinder two 25.3, and hydraulic cylinder two 25.4, wherein hydraulic cylinder one 24.1 is arranged relatively to hydraulic cylinder two 25.1, hydraulic cylinder one 24.2 is arranged relatively to hydraulic cylinder two 25.2, hydraulic cylinder one 24.3 is arranged relatively to hydraulic cylinder two 25.3, and hydraulic cylinder one 24.4 is arranged relatively to hydraulic cylinder two 25.4. Hydraulic cylinder 1 24.1 has a displacement sensor 23.1, hydraulic cylinder 1 24.2 has a displacement sensor 23.2, hydraulic cylinder 1 24.3 has a displacement sensor 23.3, hydraulic cylinder 1 24.4 has a displacement sensor 23.4, hydraulic cylinder 2 25.1 has a displacement sensor 26.1, hydraulic cylinder 2 25.2 has a displacement sensor 26.2, hydraulic cylinder 2 25.3 has a displacement sensor 26.3, and hydraulic cylinder 2 25.4 has a displacement sensor 26.4.

[0023] The comprehensive experimental system for cylinder synchronization and loading under multiple loading conditions also includes a proportional directional valve group set in conjunction with the hydraulic cylinders, wherein hydraulic cylinder 24.1 is equipped with a proportional directional valve group 16.1, hydraulic cylinder 24.2 is equipped with a proportional directional valve group 16.2, hydraulic cylinder 24.3 is equipped with a proportional directional valve group 16.3, hydraulic cylinder 24.4 is equipped with a proportional directional valve group 16.4, hydraulic cylinder 25.1 is equipped with a proportional directional valve group 22.1, hydraulic cylinder 25.2 is equipped with a proportional directional valve group 22.2, hydraulic cylinder 25.3 is equipped with a proportional directional valve group 22.3, and hydraulic cylinder 25.4 is equipped with a proportional directional valve group 22.4. The pressure oil ports of proportional directional valve group 16.1, proportional directional valve group 16.2, proportional directional valve group 16.3, proportional directional valve group 16.4, proportional directional valve group 2 22.1, proportional directional valve group 2 22.2, proportional directional valve group 2 22.3 and proportional directional valve group 2 22.4 are all connected to the hydraulic power source, so that the hydraulic oil delivered by the constant pressure variable pump 11 can enter the proportional directional valve group 16.1, proportional directional valve group 16.2, proportional directional valve group 16.3, proportional directional valve group 16.4, proportional directional valve group 2 22.1, proportional directional valve group 2 22.2, proportional directional valve group 2 22.3 and proportional directional valve group 2 22.4 through the hydraulic power source. The two working oil ports of the proportional directional valve group 16.1 are respectively connected to the rodless chamber of the hydraulic cylinder 24.1 and the rod chamber of the hydraulic cylinder 24.1. The two working oil ports of the proportional directional valve group 16.2 are respectively connected to the rodless chamber of the hydraulic cylinder 24.3 and the rod chamber of the hydraulic cylinder 24.3. The two working oil ports of the proportional directional valve group 16.3 are respectively connected to the rodless chamber of the hydraulic cylinder 24.3 and the rod chamber of the hydraulic cylinder 24.3. The two working oil ports of the two working oil ports of the proportional directional valve group 16.4 are respectively connected to the rodless chamber of the hydraulic cylinder 24.4 and the rod chamber of the hydraulic cylinder 24.4. The two working oil ports of the proportional directional valve group 22.1 are connected with the rodless chamber of the hydraulic cylinder 25.1 and the rod chamber of the hydraulic cylinder 1 25.1 respectively, the two working oil ports of the proportional directional valve group 22.2 are connected with the rodless chamber of the hydraulic cylinder 25.2 and the rod chamber of the hydraulic cylinder 1 25.2 respectively, the two working oil ports of the proportional directional valve group 22.3 are connected with the rodless chamber of the hydraulic cylinder 25.3 and the rod chamber of the hydraulic cylinder 1 25.3 respectively, the two working oil ports of the proportional directional valve group 22.4 are connected with the rodless chamber of the hydraulic cylinder 25.4 and the rod chamber of the hydraulic cylinder 1 25.4 respectively. The rod chambers of proportional directional valve group 1 16.1, proportional directional valve group 1 16.2, proportional directional valve group 1 16.3, proportional directional valve group 1 16.4, proportional directional valve group 2 22.1, proportional directional valve group 2 22.2, proportional directional valve group 2 22.3, and proportional directional valve group 2 22.4 are all connected to the oil tank 33.

[0024] Here, it should be noted that, according to needs, the proportional directional valve group 1 and the proportional directional valve group 2 can be the same proportional directional valve group, and the proportional directional valve group 1 and the proportional directional valve group 2 can also be different proportional directional valve groups. However, the proportional directional valve group 1 and the proportional directional valve group 2 in the utility model use different proportional directional valve groups.

[0025] A pressure regulating oil circuit 28 is also connected between the hydraulic power source and the rodless chambers of hydraulic cylinder 1 24.1, hydraulic cylinder 1 24.2, hydraulic cylinder 1 24.3, hydraulic cylinder 1 24.4, hydraulic cylinder 2 25.1, hydraulic cylinder 2 25.2, hydraulic cylinder 2 25.3, and hydraulic cylinder 2 25.4; a proportional pressure reducing relief valve 20.1 is installed on the pressure regulating oil circuit 28 between the hydraulic power source and the rodless chamber of hydraulic cylinder 1 24.1, and a proportional pressure reducing relief valve 20. 2. Pressure reducing relief valves are installed on the pressure regulating oil circuit 28 between the hydraulic power source and the rodless chamber of hydraulic cylinder 24.2, on the pressure regulating oil circuit 28 between the hydraulic power source and the rodless chamber of hydraulic cylinder 24.3, on the pressure regulating oil circuit 28 between the hydraulic power source and the rodless chamber of hydraulic cylinder 24.4, on the pressure regulating oil circuit 28 between the hydraulic power source and the rodless chamber of hydraulic cylinder 25.2, on the pressure regulating oil circuit 28 between the hydraulic power source and the rodless chamber of hydraulic cylinder 25.3, and on the pressure regulating oil circuit 28 between the hydraulic power source and the rodless chamber of hydraulic cylinder 25.4. That is, there are a total of 8 pressure regulating oil circuits in this electro-hydraulic system, of which 2 pressure regulating oil circuits are installed with proportional pressure reducing relief valves, which are respectively proportional pressure reducing relief valve 20.1 and proportional pressure reducing relief valve 20.2; the other 6 pressure regulating oil circuits are installed with pressure reducing relief valves, which are respectively pressure reducing relief valve 19.1, pressure reducing relief valve 19.2, pressure reducing relief valve 19.3, pressure reducing relief valve 19.4, pressure reducing relief valve 19.5 and pressure reducing relief valve 19.6.

[0026] As a further option of this embodiment, in order to facilitate the control of the pressure regulating oil circuit 28, a high-pressure stop valve is installed at the outlet end of each pressure reducing relief valve and the outlet end of each proportional pressure reducing relief valve. These high-pressure stop valves are respectively high-pressure stop valve 17.5, high-pressure stop valve 17.7, high-pressure stop valve 17.9, high-pressure stop valve 17.11, high-pressure stop valve 17.14, high-pressure stop valve 17.17, high-pressure stop valve 17.20, and high-pressure stop valve 17.24.

[0027] As a further option of this embodiment, a high-pressure stop valve is also installed between the working oil port of each proportional directional valve group one and the rodless chamber of each hydraulic cylinder one, and between the working oil port of each proportional directional valve group two and the rodless chamber of each hydraulic cylinder two. These high-pressure stop valves are respectively high-pressure stop valve 17.1, high-pressure stop valve 17.2, high-pressure stop valve 17.3, high-pressure stop valve 17.4, high-pressure stop valve 17.15, high-pressure stop valve 17.18, high-pressure stop valve 17.21, and high-pressure stop valve 17.23.

[0028] As a further option of this embodiment, a unloading oil circuit 29 is connected between the working oil port of each proportional directional valve group one and the corresponding rod chamber of the hydraulic cylinder one, and between the working oil port of each proportional directional valve group two and the corresponding rod chamber of the hydraulic cylinder two. High-pressure stop valves are also installed on these unloading oil circuits 29. These high-pressure stop valves are respectively high-pressure stop valve 17.6, high-pressure stop valve 17.8, high-pressure stop valve 17.10, high-pressure stop valve 17.12, high-pressure stop valve 17.13, high-pressure stop valve 17.16, high-pressure stop valve 17.19, and high-pressure stop valve 17.22.

[0029] As a further option of this embodiment, in order to facilitate monitoring of the hydraulic oil pressure in the oil outlet of the hydraulic power source, the rodless chamber of each hydraulic cylinder one, and the rodless chamber of each hydraulic cylinder two, pressure gauges are installed on the oil outlet of the hydraulic power source, between the rodless chamber of each hydraulic cylinder one and the hydraulic power source, and between the rodless chamber of each hydraulic cylinder two and the hydraulic power source. These pressure gauges are pressure gauge 18.1, pressure gauge 18.2, pressure gauge 18.3, pressure gauge 18.4, pressure gauge 18.5, pressure gauge 18.6, pressure gauge 18.7, pressure gauge 18.8, and pressure gauge 18.9.

[0030] As a further option of this embodiment, pressure sensors are installed on the oil outlet of the hydraulic power source, between the proportional pressure reducing relief valve 20.1 and the rodless chamber of hydraulic cylinder 1 24.1, and between the proportional pressure reducing relief valve 20.2 and the rodless chamber of hydraulic cylinder 2 25.1. These pressure sensors are pressure sensor 21.2, pressure sensor 21.1, and pressure sensor 21.3 respectively.

[0031] When this system is used to detect related functions of multi-cylinder synchronous control system:

[0032] 1. Implementation of two proportional valve control cylinder systems:

[0033] A proportional valve cylinder control system: composed of a proportional directional valve group 16.1, a hydraulic cylinder 24.1, and a displacement sensor 23.1, at which time a hydraulic cylinder 24.2, a hydraulic cylinder 24.3, and a hydraulic cylinder 24.4 can be tested synchronously, and for the convenience of description, it is named a proportional valve cylinder control system 1. At this time, high-pressure stop valves 17.1, 17.2, 17.3, and 17.4 are in an open state, and high-pressure stop valves 17.5, 17.6, 17.7, 17.8, 17.9, 17.10, 17.11, and 17.12 are in a closed state.

[0034] Another proportional valve cylinder control system: It is composed of proportional directional valve group 22.1, hydraulic cylinder 25.1, and displacement sensor 26.1. At this time, hydraulic cylinder 25.2, hydraulic cylinder 25.3, and hydraulic cylinder 25.4 can be tested synchronously. For the convenience of description, it is named proportional valve cylinder control system 2. At this time, high-pressure stop valve 17.15, high-pressure stop valve 17.18, high-pressure stop valve 17.21, and high-pressure stop valve 17.23 are in the open state, and high-pressure stop valve 17.13, high-pressure stop valve 17.14, high-pressure stop valve 17.16, high-pressure stop valve 17.17, high-pressure stop valve 17.19, high-pressure stop valve 17.20, high-pressure stop valve 17.22, and high-pressure stop valve 17.24 are in the closed state.

[0035] 2. Implementation of proportional valve control cylinder system under different load conditions:

[0036] When the hydraulic cylinder 1 24.1, hydraulic cylinder 1 24.2, hydraulic cylinder 1 24.3, and hydraulic cylinder 1 24.4 in the proportional valve control cylinder system 1 need to be loaded, the hydraulic cylinder 2 25.1, hydraulic cylinder 2 25.2, hydraulic cylinder 2 25.3, and hydraulic cylinder 2 25.4 in the proportional valve control cylinder system 2 are used to load them respectively, and the loading force of the hydraulic cylinder 1 24.1, hydraulic cylinder 1 24.2, hydraulic cylinder 1 24.3, and hydraulic cylinder 1 24.4 in the proportional valve control cylinder system 1 is determined by the hydraulic cylinder 2 25.1, hydraulic cylinder 2 25.2, hydraulic cylinder 2 25.3, and hydraulic cylinder 2 in the proportional valve control cylinder system 2. The proportional pressure reducing relief valve 20.2, pressure reducing relief valve 19.4, pressure reducing relief valve 19.5 and pressure reducing relief valve 19.6 corresponding to 25.4 are adjusted. At this time, the high-pressure stop valve 17.13, high-pressure stop valve 17.14, high-pressure stop valve 17.16, high-pressure stop valve 17.17, high-pressure stop valve 17.19, high-pressure stop valve 17.20, high-pressure stop valve 17.22 and high-pressure stop valve 17.24 are in the open state, and the high-pressure stop valve 17.15, high-pressure stop valve 17.18, high-pressure stop valve 17.21 and high-pressure stop valve 17.23 are in the closed state.

[0037] When hydraulic cylinder 25.1, hydraulic cylinder 25.2, hydraulic cylinder 25.3 and hydraulic cylinder 25.4 in proportional valve control cylinder system 2 need to be loaded, they are loaded respectively by hydraulic cylinder 1 24.1, hydraulic cylinder 1 24.2, hydraulic cylinder 1 24.3 and hydraulic cylinder 1 24.4 in proportional valve control cylinder system 1, and the loading force of hydraulic cylinder 25.1, hydraulic cylinder 25.2, hydraulic cylinder 25.3 and hydraulic cylinder 25.4 in proportional valve control cylinder system 2 is adjusted by proportional pressure reducing relief valve 20.1, pressure reducing relief valve 19.3, pressure reducing relief valve 19.2 and pressure reducing relief valve 19.1 corresponding to hydraulic cylinder 1 24.1, hydraulic cylinder 1 24.2, hydraulic cylinder 1 24.3 and hydraulic cylinder 1 24.4 in proportional valve control cylinder system 1. At this time, high-pressure stop valve 17.5, high-pressure stop valve 17.6, high-pressure stop valve 17.7, high-pressure stop valve 17.8, high-pressure stop valve 17.9, high-pressure stop valve 17.10, high-pressure stop valve 17.11, and high-pressure stop valve 17.12 are in the open state, and high-pressure stop valve 17.1, high-pressure stop valve 17.2, high-pressure stop valve 17.3, and high-pressure stop valve 17.4 are in the closed state.

[0038] When this system is used to detect the cylinder pressure control system:

[0039] 1. Implementation of proportional pressure system under different load conditions:

[0040] A proportional pressure control system: composed of a proportional pressure relief valve 20.1, a pressure sensor 21.1, and a hydraulic cylinder 24.1, for the convenience of description, it is named as a proportional pressure control system 1. At this time, the high-pressure stop valve 17.11 and the high-pressure stop valve 17.12 are in an open state, and the high-pressure stop valve 17.4 is in a closed state.

[0041] Another proportional pressure control system: It is composed of a proportional pressure relief valve 20.2, a pressure sensor 21.3, and a hydraulic cylinder 25.1. For the convenience of description, it is named proportional pressure control system 2. At this time, the high-pressure stop valve 17.13 and the high-pressure stop valve 17.1 are in the open state, and the high-pressure stop valve 17.5 is in the closed state.

[0042] There are two loading methods for loading proportional pressure control system 1: one is pressure loading, and the loading pressure is adjusted through the proportional pressure reducing relief valve 20.2 in the proportional pressure control system 2; the other is displacement loading, and the displacement is controlled by the hydraulic cylinder 2 25.1 in the proportional valve control cylinder system 2, thereby realizing displacement loading.

[0043] There are two loading methods for loading proportional pressure control system 2: one is pressure loading, and the loading pressure is adjusted through the proportional pressure reducing relief valve 20.1 in the proportional pressure control system 1; the other is displacement loading, and the displacement is controlled by the hydraulic cylinder 1 24.1 in the proportional valve control cylinder system 1, thereby realizing displacement loading.

[0044] In the description of this specification, the description with reference to the terms "one embodiment / method", "some embodiments / methods", "example", "specific example" or "some examples" etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment / method or example are included in at least one embodiment / method or example of the present application. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment / method or example. Moreover, the specific features, structures, materials or characteristics described may be combined in a suitable manner in any one or more embodiments / methods or examples. In addition, those skilled in the art may combine and combine the different embodiments / methods or examples described in this specification and the features of the different embodiments / methods or examples, unless they are contradictory.

[0045] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In the description of this application, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0046] Those skilled in the art should understand that the above embodiments are only for the purpose of clearly illustrating the present invention, and are not intended to limit the scope of the present invention. For those skilled in the art, other changes or modifications may be made based on the above disclosure, and these changes or modifications are still within the scope of the present invention.

Claims

1. A comprehensive experimental system for cylinder synchronization and loading under multiple loading conditions, characterized in that: It comprises hydraulic cylinders arranged opposite to each other, and the telescopic rods of the hydraulic cylinders are all equipped with displacement sensors; It also includes a proportional directional valve group arranged in conjunction with the hydraulic cylinder, the pressure oil port of the proportional directional valve group is connected to the hydraulic power source, the return oil port of the proportional directional valve group is connected to the oil tank, and the two working oil ports of the proportional directional valve group are respectively connected to the rodless chamber of the hydraulic cylinder and the rod chamber of the hydraulic cylinder; a pressure regulating oil circuit is also connected between the hydraulic power source and the rodless chamber of the hydraulic cylinder, and a proportional pressure reducing overflow valve is installed on the pressure regulating oil circuit.

2. The multi-loading condition oil cylinder synchronization and loading comprehensive experimental system according to claim 1 is characterized in that: There are multiple groups of hydraulic cylinders arranged relatively to each other, and each hydraulic cylinder is equipped with a proportional directional valve group. A proportional pressure reducing relief valve is installed on the pressure regulating oil circuit equipped with one group of hydraulic cylinders, and pressure reducing relief valves are installed on the pressure regulating oil circuits equipped with the remaining hydraulic cylinders.

3. The multi-loading condition cylinder synchronization and loading comprehensive experimental system according to claim 1 or 2, characterized in that: A unloading oil circuit is also connected between the working oil port of the proportional directional valve group and the rod chamber of the hydraulic cylinder, and high-pressure stop valves are installed at the outlet end of the pressure reducing relief valve, the outlet end of the proportional pressure reducing relief valve, between the working oil port of the proportional directional valve group and the rodless chamber of the hydraulic cylinder, and on the unloading oil circuit.

4. The multi-loading condition cylinder synchronization and loading comprehensive experimental system according to claim 3 is characterized in that: Pressure sensors are installed between the proportional pressure reducing relief valve and the rodless chamber of the hydraulic cylinder and on the oil outlet of the hydraulic power source.

5. The multi-loading condition oil cylinder synchronization and loading comprehensive experimental system according to claim 3 is characterized in that: Pressure gauges are installed on the rodless chamber of the hydraulic cylinder and the oil outlet of the hydraulic power source.

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