Testing device for alternating constant load and compressed gas working condition load in linear motion

Abstract

The utility model belongs to the technical field of test device design, and provides a test device for alternating constant load and compressed gas working condition load in linear motion, which comprises a driving cylinder, a load cylinder, an air pressure device and a hydraulic device, the output end of a hydraulic linear driving component is connected with one end of the driving cylinder, and the load cylinder is connected with the other end of the driving cylinder; the air pressure assembly and the hydraulic assembly provide loads for the load cylinders through switching of the servo valves. According to the utility model, the test purpose of non-stop switching of a constant load and a compressed gas working condition load in linear motion is realized, the working load working condition of the hydraulic linear driving assembly is simulated, and the performance of the hydraulic linear driving assembly is tested in a high-efficiency, high-precision, stable and reliable manner through monitoring of real-time displacement, pressure, flow and the like; performance data is provided.

Description

Technical Field

[0001] The utility model belongs to the technical field of test device design, and relates to a hydraulic linear drive component performance test device, in particular to a test device with alternating constant load and compressed gas working load in linear motion. Background Art

[0002] The factory hydraulic linear drive component load has a wide range and large load values. It also needs to provide constant load and compressed gas working load switching without stopping during linear motion. Currently, there is no suitable testing method to meet its testing requirements, making it impossible to conduct relevant performance verification and provide test data. Utility Model Content

[0003] In order to solve the above problems, the utility model provides a test device for alternating constant load and compressed gas working load in linear motion, which realizes the test purpose of providing non-stop switching between constant load and compressed gas working load in linear motion, and is used to simulate the load of hydraulic linear drive components for performance testing.

[0004] The technical solution of the utility model is as follows:

[0005] A test device for alternating constant load and compressed gas working load in linear motion includes a drive cylinder, a load cylinder, a pneumatic device and a hydraulic device. The output end of the hydraulic linear drive component is connected to one end of the drive cylinder, and the load cylinder is connected to the other end of the drive cylinder. The pneumatic component and the hydraulic component respectively provide loads for the load cylinder through the switching of a servo valve.

[0006] Furthermore, the air pressure component is a bladder accumulator.

[0007] Furthermore, the hydraulic assembly is an oil pump type hydraulic structure.

[0008] Furthermore, the hydraulic assembly includes an oil tank, an oil supply pump group and a proportional relief valve. The inlet of the oil supply pump group is connected to the oil tank, and the outlet of the oil supply pump group is connected to the load cylinder through a servo valve. The load cylinder is also connected to the oil tank through a proportional relief valve.

[0009] Furthermore, a radiator is provided on the oil line between the proportional relief valve and the oil tank.

[0010] Furthermore, an oil suction filter is provided at the inlet of the oil supply pump group, and a one-way valve and a pressure gauge are provided at the outlet of the oil supply pump group.

[0011] Technical effects of this utility model:

[0012] The above-mentioned utility model achieves the test purpose of providing constant load and compressed gas working load switching without stopping in linear motion, which is used to simulate the working load conditions of hydraulic linear drive components. Through real-time displacement, pressure, flow and other monitoring, the performance of hydraulic linear drive components is tested efficiently, accurately, stably and reliably to provide performance data. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following briefly introduces the drawings required for describing the embodiments. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0014] Figure 1 This is a schematic diagram of the principle of a test method for alternating constant load and compressed gas working load in linear motion according to the present invention;

[0015] Figure 2 This is a schematic diagram of an engineering embodiment of a test method for alternating constant load and compressed gas load in linear motion according to the utility model;

[0016] Among them, 1—hydraulic linear drive assembly, 2—flow meter, 3—first switch valve, 4—first pressure sensor, 5—drive cylinder (with displacement sensor), 6—load cylinder (with displacement sensor), 7—second pressure sensor, 8—bladder accumulator, 9—second switch valve, 10—servo valve, 11—third pressure sensor, 12—filter, 13—check valve, 14—pressure gauge, 15—oil supply pump group, 16—third switch valve, 17—oil suction filter, 18—safety valve, 19—proportional relief valve, 20—radiator, 21—liquid level gauge, 22—breathing filter, 23—temperature sensor, 24—oil drain valve, 25—oil tank, 26—schematic diagram of hydraulic load assembly, 27—schematic diagram of hydraulic linear drive assembly, 28—schematic diagram of top cylinder assembly, 29—schematic diagram of bladder accumulator assembly. DETAILED DESCRIPTION

[0017] This section is an embodiment of the present invention, which is used to explain and illustrate the technical solution of the present invention. In the absence of conflict, the embodiments of the present invention and the features in the embodiments can be combined with each other.

[0018] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside" and the like indicating directions or positional relationships are based on the orientations or positional relationships in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and are not intended to indicate or imply that the device or case referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention. In addition, the terms "first", "second" and the like are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implying the number of technical features indicated. Therefore, features defined as "first", "second" and the like may explicitly or implicitly include more of such features. In the description of the present invention, unless otherwise specified, "multiple" means two or more.

[0019] In the description of this utility model, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be interpreted broadly. For example, they can refer to fixed connections, detachable connections, or integrated connections; mechanical connections, point connections; direct connections, indirect connections through an intermediate medium, and internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in this utility model based on specific circumstances.

[0020] Example 1:

[0021] A test device for alternating constant load and compressed gas working load in linear motion includes a drive cylinder 5, a load cylinder 6, a pneumatic device and a hydraulic device. The output end of the hydraulic linear drive component 1 is connected to one end of the drive cylinder 5, and the load cylinder 6 is connected to the other end of the drive cylinder. The pneumatic component and the hydraulic component respectively provide loads for the load cylinder 6 through the switching of the servo valve 10.

[0022] The air pressure component is a bladder accumulator 8.

[0023] The hydraulic assembly is an oil pump type hydraulic structure.

[0024] The hydraulic assembly includes an oil tank 25, an oil supply pump group 15 and a proportional relief valve 19. The inlet of the oil supply pump group 15 is connected to the oil tank 25, and the outlet of the oil supply pump group 15 is connected to the load cylinder 6 through the servo valve 10. The load cylinder 6 is also connected to the oil tank 25 through the proportional relief valve 19.

[0025] A radiator 20 is provided on the oil path between the proportional relief valve 19 and the oil tank 25 .

[0026] An oil suction filter 17 is provided at the inlet of the oil supply pump group 15 , and a one-way valve 13 and a pressure gauge 14 are provided at the outlet of the oil supply pump group 15 .

[0027] A test device for alternating constant load and compressed gas load in linear motion according to the present invention:

[0028] The hydraulic load system outputs variable pressure to control the top cylinder to achieve constant high load simulation in reciprocating linear motion, and realize real-time monitoring of displacement, pressure and flow;

[0029] The bladder accumulator is used to simulate the working load of compressed gas in reciprocating linear motion, and to achieve real-time monitoring of displacement, pressure and flow.

[0030] The stable switching of load types during reciprocating motion is achieved by shutting off the servo valve.

[0031] Example 2:

[0032] Figure 1 The utility model is a schematic diagram of the principle of a test method for alternating constant load and compressed gas working load in linear motion.

[0033] refer to Figure 1 As shown in the figure above, the oil supply pump group 15 sucks the load medium from the oil tank 25 through the oil suction filter 17 and the switch valve 16. After being pressurized by the oil supply pump group 15, the load medium enters the load cylinder (with displacement sensor) 6 through the one-way valve 13, the filter 12, the servo valve 10, and the bladder accumulator 8. The system return oil returns to the oil tank 25 through the proportional relief valve 19 and the radiator 20.

[0034] The principle proportional relief valve 19 adjusts the pressure before the servo valve 10, and controls the pressure in the load cylinder (with displacement sensor) 6 and the inflow and outflow of the load medium through the servo valve. The oil supply pump group 15 is driven by a variable frequency motor, which can assist in adjusting the oil supply flow. The principle bypass safety valve 18 sets the maximum load pressure to prevent the load from overpressure, and the return oil circuit is equipped with a radiator 20 to prevent the load from overheating. The principle is equipped with two-stage filtering devices, namely the oil suction filter 17 and the oil supply filter 12, to ensure that the cleanliness of the oil entering the servo valve 10 and the load cylinder (with displacement sensor) 6 meets the use requirements. The load oil storage tank 25 is equipped with a breathing filter 22, a liquid level meter 21, a temperature sensor 23 and an oil drain valve 25.

[0035] In the principle, the driving cylinder (with displacement sensor) 5 and the load cylinder (with displacement sensor) 6 are connected in the form of top cylinders, and the driving cylinder (with displacement sensor) 5 is connected to the hydraulic linear drive component 1.

[0036] The principle is equipped with a flow meter 2, a pressure sensor 4, a pressure sensor 7, a pressure sensor 11, a pressure gauge 14, a liquid level meter 21, a temperature sensor 23 and a displacement sensor built into the drive cylinder (with a displacement sensor) 5 and the load cylinder (with a displacement sensor) 6, which can monitor key parameters such as drive pressure and displacement in real time.

[0037] Description of the load simulation test process: Before the test begins, the rodless chamber pressure of the load cylinder (with displacement sensor) 6 is adjusted to meet the constant load. During the operation of the hydraulic linear drive assembly 1, the drive cylinder (with displacement sensor) 5 extends, and the load cylinder (with displacement sensor) 6 contracts, the oil supply pump group 15 continuously outputs the load medium. Through the combined action of the servo valve 10 and the proportional relief valve 1, the rodless chamber pressure of the load cylinder (with displacement sensor) 6 is maintained to achieve the simulation of the constant load in the linear motion. During the test, when it is necessary to simulate the compressed gas working condition load, the servo valve 10 is directly closed. At this time, as the linear motion continues, the load is provided by the compressed air in the bladder of the bladder accumulator 8. The load form is replaced to achieve the simulation of the compressed gas working condition load.

[0038] In some embodiments, by setting parameters such as load pressure and top cylinder displacement, a test method for alternating constant load and compressed gas working load in linear motion can be used for working performance testing of other types of hydraulic linear drive component products, and constant load or compressed gas working load simulation can be performed separately.

[0039] In some embodiments, a test method for alternating constant load and compressed gas working load in linear motion can be used to perform performance tests such as reverse pressure resistance and sealing performance of hydraulic linear drive component products. The load medium is continuously output by the oil supply pump group 15, and the servo valve 10 and the proportional relief valve 1 work together to maintain the rodless chamber pressure of the load cylinder (with displacement sensor) 6, and the load cylinder (with displacement sensor) 6 is extended and the drive cylinder (with displacement sensor) 5 is retracted to achieve this.

[0040] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, but the protection scope of the present invention is not limited thereto. Any technician familiar with the field can easily think of various equivalent modifications or replacements within the technical scope disclosed in the present invention, and these modifications or replacements should all be included in the protection scope of the present invention.

Claims

1. A test device for alternating constant load and compressed gas load in linear motion, characterized in that: The invention comprises a driving cylinder (5), a load cylinder (6), a pneumatic device and a hydraulic device. The output end of the hydraulic linear driving component (1) is connected to one end of the driving cylinder (5), and the load cylinder (6) is connected to the other end of the driving cylinder. The pneumatic component and the hydraulic component respectively provide loads for the load cylinder (6) through the switching of a servo valve (10).

2. A test device for alternating constant load and compressed gas load in linear motion according to claim 1, characterized in that: The air pressure component is a bladder accumulator (8).

3. The test device for alternating constant load and compressed gas load in linear motion according to claim 1, characterized in that: The hydraulic assembly is an oil pump type hydraulic structure.

4. A test device for alternating constant load and compressed gas load in linear motion according to claim 3, characterized in that: The hydraulic assembly comprises an oil tank (25), an oil supply pump group (15) and a proportional relief valve (19). The inlet of the oil supply pump group (15) is connected to the oil tank (25), and the outlet of the oil supply pump group (15) is connected to the load cylinder (6) through a servo valve (10). The load cylinder (6) is also connected to the oil tank (25) through the proportional relief valve (19).

5. The test device for alternating constant load and compressed gas load in linear motion according to claim 4, characterized in that: A radiator (20) is provided on the oil path between the proportional relief valve (19) and the oil tank (25).

6. The test device for alternating constant load and compressed gas load in linear motion according to claim 4, characterized in that: An oil suction filter (17) is provided at the inlet of the oil supply pump group (15), and a one-way valve (13) and a pressure gauge (14) are provided at the outlet of the oil supply pump group (15).

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