Composite pipe four-point composite loading hydraulic control system

Abstract

The invention belongs to the technical field of test loading equipment, and particularly provides a composite pipe four-point composite loading hydraulic control system which comprises a main hydraulic cylinder control module, an axial hydraulic cylinder control module and a pressure source control module. The main hydraulic cylinder control module comprises a first main hydraulic cylinder, a second main hydraulic cylinder and a first electro-hydraulic directional control valve; the axial hydraulic cylinder control module comprises a first axial hydraulic cylinder, a second axial hydraulic cylinder, a second electro-hydraulic directional control valve and a third electro-hydraulic directional control valve; a pressure oil port P of the pressure source control module is respectively connected with an oil inlet of the first electro-hydraulic directional valve, an oil inlet of the second electro-hydraulic directional valve and an oil inlet of the third electro-hydraulic directional valve; the problem that bending and drawing force of an existing bimetal composite pipe cannot be compositely and stably loaded is solved. The four-point bending and stretching combined loading device is simple in structure, safe and reliable in operation and flexible and adjustable in operation speed, and four-point bending and stretching combined loading of the bimetal composite pipe under different pressure values can be achieved through a single pressure source.

Description

Technical Field

[0001] The invention belongs to the technical field of test loading equipment, and in particular relates to a composite pipe four-point composite loading hydraulic control system. Background Art

[0002] After the bimetallic composite pipe for oil and gas transportation is formed by hydraulic composite liquid expansion, it is usually necessary to perform a cyclic bending tensile test to detect the composite strength and mechanical properties of the composite pipe. During the four-point bending tensile test, the main hydraulic cylinder pushes and pulls the two hinge points in the middle of the composite pipe to achieve forward and reverse cyclic bending. The single bending force hinge point is ≥1000T. The axial hydraulic cylinder is used to apply symmetrical tension to the two hinge points at the end of the composite pipe. The single tensile force hinge point is ≥500T.

[0003] In order to simplify the equipment structure, when the axial force requirement is large (≥500T), a labor-saving lever structure is usually used to effectively reduce the axial force at the output end. Since the curvature radius of the composite pipe is always changing during the cyclic bending process, in order to keep the axial tension of the composite pipe constant, the pressure value of the axial force loading cylinder needs to change continuously according to the curvature radius of the composite pipe.

[0004] According to the specific process requirements of the four-point bending composite loading test, a suitable hydraulic system needs to be configured to ensure that the equipment runs smoothly, safely and reliably, and the bending force and axial tension output of the composite pipe are stable and without fluctuation.

[0005] The Chinese patent document with publication number CN115655915A discloses a four-point bending test machine for residual stress, including a support, a support arm and an actuating cylinder are arranged on the support, the actuating cylinder is arranged between the support arms, the movable end of the actuating cylinder is connected to a supporting device, and a force-applying device is arranged on the supporting device. The document belongs to the field of material analysis and testing technology, specifically refers to a four-point bending test machine for residual stress, which obtains a large area of ​​stable stress field on the surface of the workpiece through the four-point bending mechanics principle and reaction frame design, and through controllable directional loading, the residual stress calibration space is open to the outside, and the operation is convenient. The device in the document is not suitable for detecting the composite strength and mechanical properties of composite pipes. Summary of the invention

[0006] The invention provides a composite pipe four-point composite loading hydraulic control system, aiming to overcome the problem in the prior art that the bending and tensile forces of the bimetallic composite pipe cannot be compositely and stably loaded.

[0007] To this end, the present invention provides a composite pipe four-point composite loading hydraulic control system, including a main hydraulic cylinder control module, an axial hydraulic cylinder control module and a pressure source control module; the main hydraulic cylinder control module includes a first main hydraulic cylinder, a second main hydraulic cylinder and a first electro-hydraulic reversing valve; the axial hydraulic cylinder control module includes a first axial hydraulic cylinder, a second axial hydraulic cylinder, a second electro-hydraulic reversing valve and a third electro-hydraulic reversing valve; the pressure oil port P of the pressure source control module is respectively connected to the oil inlet of the first electro-hydraulic reversing valve, the oil inlet of the second electro-hydraulic reversing valve and the oil inlet of the third electro-hydraulic reversing valve, the oil outlet of the first electro-hydraulic reversing valve is respectively connected to the first main hydraulic cylinder and the second main hydraulic cylinder, the oil outlet of the second electro-hydraulic reversing valve is connected to the first axial hydraulic cylinder, the oil outlet of the third electro-hydraulic reversing valve is connected to the second axial hydraulic cylinder, and the oil return port of the first electro-hydraulic reversing valve, the oil return port of the second electro-hydraulic reversing valve and the oil return port of the third electro-hydraulic reversing valve are all connected to the oil return port T of the pressure source control module.

[0008] Preferably, the master hydraulic cylinder control module also includes a first overflow valve, and the axial hydraulic cylinder control module also includes a second overflow valve and a third overflow valve; the oil inlet of the first overflow valve is connected to the oil outlet of the first electro-hydraulic reversing valve, the oil outlet of the second electro-hydraulic reversing valve is connected to the rodless chamber A3 of the first axial hydraulic cylinder via the second overflow valve, the oil outlet of the third electro-hydraulic reversing valve is connected to the rodless chamber A4 of the second axial hydraulic cylinder via the third overflow valve, and the oil return port of the first electro-hydraulic reversing valve, the oil return port of the second electro-hydraulic reversing valve, the oil return port of the third electro-hydraulic reversing valve, the overflow port of the first overflow valve, the overflow port of the second overflow valve and the overflow port of the third overflow valve are all connected to the oil return port T of the pressure source control module.

[0009] Preferably, the master hydraulic cylinder control module further includes a first one-way speed regulating valve, a second one-way speed regulating valve, a third one-way speed regulating valve and a fourth one-way speed regulating valve, one oil outlet of the first electro-hydraulic reversing valve is connected to the rodless chamber A1 of the first master hydraulic cylinder through the first one-way speed regulating valve, two oil outlets of the first electro-hydraulic reversing valve are connected to the rod chamber B1 of the first master hydraulic cylinder through the second one-way speed regulating valve, three oil outlets of the first electro-hydraulic reversing valve are connected to the rodless chamber A2 of the second master hydraulic cylinder through the third one-way speed regulating valve, and four oil outlets of the first electro-hydraulic reversing valve are connected to the rod chamber B2 of the second master hydraulic cylinder through the fourth one-way speed regulating valve;

[0010] The axial hydraulic cylinder control module also includes a fifth one-way speed regulating valve, a sixth one-way speed regulating valve, a seventh one-way speed regulating valve and an eighth one-way speed regulating valve; one oil outlet of the second electro-hydraulic reversing valve is connected to the rodless chamber A3 of the first axial hydraulic cylinder through the second overflow valve and the fifth one-way speed regulating valve, and the second oil outlet of the second electro-hydraulic reversing valve is connected to the rod chamber B3 of the first axial hydraulic cylinder through the sixth one-way speed regulating valve;

[0011] One oil outlet of the third electro-hydraulic reversing valve is connected to the rodless chamber A4 of the second axial hydraulic cylinder through the third overflow valve and the seventh one-way speed regulating valve, and the second oil outlet of the third electro-hydraulic reversing valve is connected to the rod chamber B4 of the second axial hydraulic cylinder through the eighth one-way speed regulating valve.

[0012] Preferably, the master hydraulic cylinder control module further includes a first electromagnetic ball valve, a second electromagnetic ball valve, a third electromagnetic ball valve and a fourth electromagnetic ball valve; the first electromagnetic ball valve is connected between the first one-way speed regulating valve and the first electro-hydraulic reversing valve, the second electromagnetic ball valve is connected between the second one-way speed regulating valve and the first electro-hydraulic reversing valve, the third electromagnetic ball valve is connected between the third one-way speed regulating valve and the first electro-hydraulic reversing valve, and the fourth electromagnetic ball valve is connected between the fourth one-way speed regulating valve and the first electro-hydraulic reversing valve;

[0013] The axial hydraulic cylinder control module also includes a fifth electromagnetic ball valve and a sixth electromagnetic ball valve. The fifth electromagnetic ball valve is connected between the second overflow valve and the second electro-hydraulic reversing valve. The sixth electromagnetic ball valve is connected between the third overflow valve and the third electro-hydraulic reversing valve.

[0014] Preferably, the master hydraulic cylinder control module also includes a seventh solenoid ball valve, a ninth one-way speed regulating valve, an eighth solenoid ball valve and a tenth one-way speed regulating valve. The seventh solenoid ball valve and the ninth one-way speed regulating valve are connected in parallel between the rodless chamber A1 of the first master hydraulic cylinder and the rod chamber B1 of the first master hydraulic cylinder, and the eighth solenoid ball valve and the tenth one-way speed regulating valve are connected in parallel between the rodless chamber A2 of the second master hydraulic cylinder and the rod chamber B2 of the second master hydraulic cylinder.

[0015] Preferably, the axial hydraulic cylinder control module further includes a proportional overflow pressure reducing valve, and the pressure oil port P of the pressure source control module is respectively connected to the oil inlet of the second electro-hydraulic reversing valve and the oil inlet of the third electro-hydraulic reversing valve through the proportional overflow pressure reducing valve.

[0016] Preferably, the axial hydraulic cylinder control module also includes a second pressure gauge and a second pressure sensor, and the proportional relief pressure reducing valve is connected to the oil inlet of the second electro-hydraulic reversing valve and the oil inlet of the third electro-hydraulic reversing valve respectively through the second pressure gauge and the second pressure sensor.

[0017] Preferably, the pressure source control module includes a constant pressure variable pump, a one-way valve and a high-pressure oil filter. The pressure oil port of the pressure source control module is connected to the oil inlet of the first electro-hydraulic reversing valve and the oil inlet of the proportional overflow pressure reducing valve respectively after passing through the constant pressure variable pump, the one-way valve and the high-pressure oil filter.

[0018] Preferably, the pressure source control module also includes an oil return filter, and the oil return port of the first electro-hydraulic reversing valve, the oil return port of the second electro-hydraulic reversing valve, the oil return port of the third electro-hydraulic reversing valve, the overflow port of the first overflow valve, the overflow port of the second overflow valve and the overflow port of the third overflow valve are all connected to the oil inlet of the oil return filter after being merged through a pipeline, and the oil outlet of the oil return filter is connected to the oil return port T of the pressure source control module.

[0019] Preferably, the pressure source control module further comprises an electromagnetic overflow valve, and the electromagnetic overflow valve is connected to the main pipeline of the oil inlet of the return oil filter.

[0020] Beneficial effects of the present invention:

[0021] 1. The composite pipe four-point composite loading hydraulic control system provided by the present invention comprises a master hydraulic cylinder control module, an axial hydraulic cylinder control module and a pressure source control module; the master hydraulic cylinder control module comprises a first master hydraulic cylinder, a second master hydraulic cylinder and a first electro-hydraulic reversing valve; the axial hydraulic cylinder control module comprises a first axial hydraulic cylinder, a second axial hydraulic cylinder, a second electro-hydraulic reversing valve and a third electro-hydraulic reversing valve; the pressure source control module provides pressure to the master hydraulic cylinder control module and the axial hydraulic cylinder control module; when the bimetallic composite pipe is compositely loaded, the first electro-hydraulic reversing valve controls the forward and reverse movements of the first master hydraulic cylinder and the second master hydraulic cylinder, and the first master hydraulic cylinder and The second main hydraulic cylinder makes the composite pipe perform positive and reverse bending movements in the vertical direction through the first bending force hinge point B and the second bending force hinge point C; at the same time, the direction of the first axial hydraulic cylinder is controlled by the second electro-hydraulic reversing valve, and the direction of the second axial hydraulic cylinder is controlled by the third electro-hydraulic reversing valve. The first axial hydraulic cylinder and the second axial hydraulic cylinder extend piston rods to make points G and H move inward, and make the AG lever rotate around points E and F, thereby applying axial tension to points A and D of the composite pipe; the structure is simple, the operation is safe and reliable, and the operation speed is flexible and adjustable; the present invention uses a single pressure source to achieve four-point bending and tensile composite loading of the bimetallic composite pipe under different pressure values.

[0022] 2. In the composite pipe four-point composite loading hydraulic control system provided by the present invention, the pressure oil port P of the pressure source control module is respectively connected to the oil inlet of the second electro-hydraulic reversing valve and the oil inlet of the third electro-hydraulic reversing valve through a proportional overflow pressure reducing valve, which can effectively control the system pressure of the axial hydraulic cylinder control module. When the composite pipe is cyclically bent, the axial tension of the bimetallic composite pipe at points A and D is guaranteed to be stable by providing appropriate system pressure.

[0023] 3. In the composite pipe four-point composite loading hydraulic control system provided by the present invention, the master hydraulic cylinder control module plays a differential role on the first master hydraulic cylinder through the seventh electromagnetic ball valve and the ninth one-way speed regulating valve, and plays a differential role on the second master hydraulic cylinder through the eighth electromagnetic ball valve and the tenth one-way speed regulating valve, thereby ensuring that the piston rods of the first master hydraulic cylinder and the second master hydraulic cylinder extend quickly and at adjustable speed. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The present invention will be further described in detail below with reference to the accompanying drawings.

[0025] Figure 1 It is the hydraulic principle diagram of the present invention;

[0026] Figure 2 It is a mechanical principle diagram of the present invention.

[0027] Description of reference numerals:

[0028] P, pressure oil port of pressure source control module; T, return oil port of pressure source control module;

[0029] 1. Constant pressure variable pump, 2. Return oil filter, 301. First high pressure ball valve, 302. Second high pressure ball valve, 303. Third high pressure ball valve, 401. First pressure gauge, 402. Second pressure gauge, 403. Third pressure gauge, 501. First pressure sensor, 502. Second pressure sensor, 6. Check valve, 7. Solenoid relief valve, 8. High pressure filter, 9. Proportional relief pressure reducing valve, 101. First relief valve, 102. Second relief valve, 103. Third relief valve, 1101. First electro-hydraulic reversing valve, 1102. Second electro-hydraulic reversing valve, 1103. Third electro-hydraulic reversing valve, 1201. First electromagnetic ball valve, 1202. Second electromagnetic ball valve, 1203. Third electromagnetic ball valve, 1204. Fourth electromagnetic ball valve, 1205. Fifth electromagnetic ball valve, 12 06. The sixth electromagnetic ball valve, 1207. The seventh electromagnetic ball valve, 1208. The eighth electromagnetic ball valve, 1301. The first one-way speed regulating valve, 1302. The second one-way speed regulating valve, 1303. The third one-way speed regulating valve, 1304. The fourth one-way speed regulating valve, 1305. The fifth one-way speed regulating valve, 1306. The sixth one-way speed regulating valve, 1307. The seventh one-way speed regulating valve, 1308. The eighth one-way speed regulating valve, 1309. The ninth one-way speed regulating valve, 1310. The tenth one-way speed regulating valve, 1401. The first displacement sensor, 1402. The second displacement sensor, 1403. The third displacement sensor, 1404. The fourth displacement sensor, 1501. The first master hydraulic cylinder, 1502. The second master hydraulic cylinder, 1601. The first axial hydraulic cylinder, 1602. The second axial hydraulic cylinder;

[0030] A-first axial tension hinge point, D-second axial tension hinge point, B-first bending force hinge point, C-second bending force hinge point, E-first fixed support point, F-second fixed support point, G-first axial hydraulic cylinder hinge point, H-second axial hydraulic cylinder hinge point. DETAILED DESCRIPTION

[0031] The principles and features of the present invention are described below in conjunction with the accompanying drawings. The examples given are only used to explain the present invention and are not used to limit the scope of the present invention.

[0032] Embodiment 1:

[0033] like Figure 1 and Figure 2 As shown, a composite pipe four-point composite loading hydraulic control system includes a main hydraulic cylinder control module, an axial hydraulic cylinder control module and a pressure source control module; the main hydraulic cylinder control module includes a first main hydraulic cylinder 1501, a second main hydraulic cylinder 1502 and a first electro-hydraulic reversing valve 1101; the axial hydraulic cylinder control module includes a first axial hydraulic cylinder 1601, a second axial hydraulic cylinder 1602, a second electro-hydraulic reversing valve 1102 and a third electro-hydraulic reversing valve 1103; the pressure oil port P of the pressure source control module is respectively connected to the oil inlet of the first electro-hydraulic reversing valve 1101, the second electro-hydraulic reversing valve 1103 and the pressure oil port P of the pressure source control module. The oil inlet of the reversing valve 1102 and the oil inlet of the third electro-hydraulic reversing valve 1103, and the oil outlet of the first electro-hydraulic reversing valve 1101 are respectively connected to the first master hydraulic cylinder 1501 and the second master hydraulic cylinder 1502, the oil outlet of the second electro-hydraulic reversing valve 1102 is connected to the first axial hydraulic cylinder 1601, and the oil outlet of the third electro-hydraulic reversing valve 1103 is connected to the second axial hydraulic cylinder 1602, and the oil return port of the first electro-hydraulic reversing valve 1101, the oil return port of the second electro-hydraulic reversing valve 1102 and the oil return port of the third electro-hydraulic reversing valve 1103 are all connected to the oil return port T of the pressure source control module.

[0034] Specifically, the pressure is provided to the main hydraulic cylinder control module and the axial hydraulic cylinder control module through the pressure source control module; when the bimetallic composite pipe is compositely loaded, the first electro-hydraulic reversing valve 1101 is controlled to control the forward and reverse movements of the first master hydraulic cylinder 1501 and the second master hydraulic cylinder 1502, and the first master hydraulic cylinder 1501 and the second master hydraulic cylinder 1502 make the composite pipe perform forward and reverse bending movements in the vertical direction through the first bending force hinge point B and the second bending force hinge point C; at the same time, the second electro-hydraulic reversing valve 1102 is controlled to The direction of the first axial hydraulic cylinder 1601 is controlled, and the direction of the second axial hydraulic cylinder 1602 is controlled by the third electro-hydraulic reversing valve 1103. The first axial hydraulic cylinder 1601 and the second axial hydraulic cylinder 1602 extend piston rods to move points G and H inward, and the AG lever rotates around points E and F, thereby applying axial tension to points A and D of the composite pipe; the structure is simple, the operation is safe and reliable, and the operation speed is flexible and adjustable; the present invention uses a single pressure source to achieve four-point bending and tensile composite loading of the bimetallic composite pipe under different pressure values.

[0035] Preferably, the master hydraulic cylinder control module also includes a first overflow valve 101, and the axial hydraulic cylinder control module also includes a second overflow valve 102 and a third overflow valve 103; the oil inlet of the first overflow valve 101 is connected to the oil outlet of the first electro-hydraulic reversing valve 1101, the oil outlet of the second electro-hydraulic reversing valve 1102 is connected to the rodless chamber A3 of the first axial hydraulic cylinder 1601 via the second overflow valve 102, the oil outlet of the third electro-hydraulic reversing valve 1103 is connected to the rodless chamber A4 of the second axial hydraulic cylinder 1602 via the third overflow valve 103, and the oil return port of the first electro-hydraulic reversing valve 1101, the oil return port of the second electro-hydraulic reversing valve 1102, the oil return port of the third electro-hydraulic reversing valve 1103, the overflow port of the first overflow valve 101, the overflow port of the second overflow valve 102 and the overflow port of the third overflow valve 103 are all connected to the oil return port T of the pressure source control module.

[0036] Specifically, the first overflow valve 101 is a pressure protection valve on the rodless cavity side of the first master hydraulic cylinder 1501 and the rodless cavity side of the second master hydraulic cylinder 1502, the second overflow valve 102 is a pressure protection valve on the rodless cavity side of the first axial hydraulic cylinder 1601, and the third overflow valve 103 is a pressure protection valve on the rodless cavity side of the second axial hydraulic cylinder 1602, thereby ensuring the safety of the master hydraulic cylinder control module when in use.

[0037] Preferably, the master hydraulic cylinder control module further includes a first one-way speed regulating valve 1301, a second one-way speed regulating valve 1302, a third one-way speed regulating valve 1303 and a fourth one-way speed regulating valve 1304, one oil outlet of the first electro-hydraulic reversing valve 1101 is connected to the rodless chamber A1 of the first master hydraulic cylinder 1501 through the first one-way speed regulating valve 1301, two oil outlets of the first electro-hydraulic reversing valve 1101 are connected to the rod chamber B1 of the first master hydraulic cylinder 1501 through the second one-way speed regulating valve 1302, three oil outlets of the first electro-hydraulic reversing valve 1101 are connected to the rodless chamber A2 of the second master hydraulic cylinder 1502 through the third one-way speed regulating valve 1303, and four oil outlets of the first electro-hydraulic reversing valve 1101 are connected to the rod chamber B2 of the second master hydraulic cylinder 1502 through the fourth one-way speed regulating valve 1304;

[0038] The axial hydraulic cylinder control module also includes a fifth one-way speed regulating valve 1305, a sixth one-way speed regulating valve 1306, a seventh one-way speed regulating valve 1307 and an eighth one-way speed regulating valve 1308; one oil outlet of the second electro-hydraulic reversing valve 1102 is connected to the rodless chamber A3 of the first axial hydraulic cylinder 1601 through the second overflow valve 102 and the fifth one-way speed regulating valve 1305, and the second oil outlet of the second electro-hydraulic reversing valve 1102 is connected to the rod chamber B3 of the first axial hydraulic cylinder 1601 through the sixth one-way speed regulating valve 1306;

[0039] One oil outlet of the third electro-hydraulic reversing valve 1103 is connected to the rodless chamber A4 of the second axial hydraulic cylinder 1602 through the third overflow valve 103 and the seventh one-way speed regulating valve 1307, and the second oil outlet of the third electro-hydraulic reversing valve 1103 is connected to the rod chamber B4 of the second axial hydraulic cylinder 1602 through the eighth one-way speed regulating valve 1308.

[0040] Specifically, the first one-way speed regulating valve 1301 and the second one-way speed regulating valve 1302 are used to facilitate the control of the extension and retraction speed of the piston rod of the first master hydraulic cylinder 1501; the third one-way speed regulating valve 1303 and the fourth one-way speed regulating valve 1304 are used to facilitate the control of the extension and retraction speed of the piston rod of the second master hydraulic cylinder 1502; the fifth one-way speed regulating valve 1305 and the sixth one-way speed regulating valve 1306 are used to facilitate the control of the extension and retraction speed of the piston rod of the first axial hydraulic cylinder 1601; the seventh one-way speed regulating valve 1307 and the eighth one-way speed regulating valve 1308 are used to facilitate the control of the extension and retraction speed of the piston rod of the second axial hydraulic cylinder 1602.

[0041] Preferably, the master hydraulic cylinder control module further includes a first electromagnetic ball valve 1201, a second electromagnetic ball valve 1202, a third electromagnetic ball valve 1203 and a fourth electromagnetic ball valve 1204; the first electromagnetic ball valve 1201 is connected between the first one-way speed regulating valve 1301 and the first electro-hydraulic reversing valve 1101, the second electromagnetic ball valve 1202 is connected between the second one-way speed regulating valve 1302 and the first electro-hydraulic reversing valve 1101, the third electromagnetic ball valve 1203 is connected between the third one-way speed regulating valve 1303 and the first electro-hydraulic reversing valve 1101, and the fourth electromagnetic ball valve 1204 is connected between the fourth one-way speed regulating valve 1304 and the first electro-hydraulic reversing valve 1101;

[0042] The axial hydraulic cylinder control module further includes a fifth solenoid ball valve 1205 and a sixth solenoid ball valve 1206 . The fifth solenoid ball valve 1205 is connected between the second relief valve 102 and the second electro-hydraulic reversing valve 1102 . The sixth solenoid ball valve 1206 is connected between the third relief valve 103 and the third electro-hydraulic reversing valve 1103 .

[0043] Specifically, the first electromagnetic ball valve 1201, the second electromagnetic ball valve 1202, the third electromagnetic ball valve 1203, the fourth electromagnetic ball valve 1204, the fifth electromagnetic ball valve 1205 and the sixth electromagnetic ball valve 1206 are all safety protection valves for accidents, ensuring that all hydraulic cylinders remain in action when an accident occurs.

[0044] Preferably, the master hydraulic cylinder control module also includes a seventh solenoid ball valve 1207, a ninth one-way speed regulating valve 1309, an eighth solenoid ball valve 1208 and a tenth one-way speed regulating valve 1310. The seventh solenoid ball valve 1207 and the ninth one-way speed regulating valve 1309 are connected in parallel between the rodless chamber A1 of the first master hydraulic cylinder 1501 and the rod chamber B1 of the first master hydraulic cylinder 1501. The eighth solenoid ball valve 1208 and the tenth one-way speed regulating valve 1310 are connected in parallel between the rodless chamber A2 of the second master hydraulic cylinder 1502 and the rod chamber B2 of the second master hydraulic cylinder 1502.

[0045] Specifically, the master hydraulic cylinder control module plays a differential role on the first master hydraulic cylinder 1501 through the seventh electromagnetic ball valve 1207 and the ninth one-way speed regulating valve 1309, and plays a differential role on the second master hydraulic cylinder 1502 through the eighth electromagnetic ball valve 1208 and the tenth one-way speed regulating valve 1310, ensuring that the piston rods of the first master hydraulic cylinder 1501 and the second master hydraulic cylinder 1502 are extended quickly and at adjustable speed.

[0046] Preferably, the axial hydraulic cylinder control module also includes a proportional overflow pressure reducing valve 9, and the pressure oil port P of the pressure source control module is connected to the oil inlet of the second electro-hydraulic reversing valve 1102 and the oil inlet of the third electro-hydraulic reversing valve 1103 respectively through the proportional overflow pressure reducing valve 9.

[0047] Specifically, the pressure oil port P of the pressure source control module is connected to the oil inlet of the second electro-hydraulic reversing valve 1102 and the oil inlet of the third electro-hydraulic reversing valve 1103 respectively through the proportional overflow pressure reducing valve 9, which can effectively control the system pressure of the axial hydraulic cylinder control module. When the composite pipe is cyclically bent, the axial tension of the bimetallic composite pipe at points A and D is guaranteed to be stable by providing appropriate system pressure.

[0048] Preferably, the axial hydraulic cylinder control module also includes a second pressure gauge 402 and a second pressure sensor 502, and the proportional relief pressure reducing valve 9 is connected to the oil inlet of the second electro-hydraulic reversing valve 1102 and the oil inlet of the third electro-hydraulic reversing valve 1103 through the second pressure gauge 402 and the second pressure sensor 502 respectively.

[0049] Specifically, the second pressure gauge 402 and the second pressure sensor 502 are used to detect the pressure at the output end of the pump head and the output end pressure of the constant pressure variable pump 1; the second pressure gauge 402 and the second pressure sensor 502 are used to detect the pressure of the axial hydraulic cylinder control module; the third pressure gauge 403 and the third pressure sensor are used to detect the pressure of the main hydraulic cylinder control module.

[0050] Preferably, the first master hydraulic cylinder 1501 is also equipped with a first displacement sensor 1401 , the second master hydraulic cylinder 1502 is also equipped with a second displacement sensor 1402 , the first axial hydraulic cylinder 1601 is also equipped with a third displacement sensor 1403 , and the second axial hydraulic cylinder 1602 is also equipped with a fourth displacement sensor 1404 .

[0051] Specifically, the first displacement sensor 1401 facilitates the accurate measurement of the displacement of the piston rod of the first master hydraulic cylinder 1501; the second displacement sensor 1402 facilitates the accurate measurement of the displacement of the piston rod of the second master hydraulic cylinder 1502; the third displacement sensor 1403 facilitates the accurate measurement of the displacement of the piston rod of the first axial hydraulic cylinder 1601; and the fourth displacement sensor 1404 facilitates the accurate measurement of the displacement of the piston rod of the second axial hydraulic cylinder 1602.

[0052] Preferably, the pressure source control module includes a constant pressure variable pump 1, a one-way valve 6 and a high-pressure oil filter 8. The pressure oil port of the pressure source control module is connected to the oil inlet of the first electro-hydraulic reversing valve 1101 and the oil inlet of the proportional overflow pressure reducing valve 9 respectively after passing through the constant pressure variable pump 1, the one-way valve 6 and the high-pressure oil filter 8 in sequence.

[0053] Specifically, the constant pressure variable pump 1 ensures that the pressure of the supplied pressure oil is stable, the one-way valve 6 ensures that the pressure oil flows along the established pipeline to prevent oil return; the high-pressure oil filter 8 is convenient for filtering out impurities in the pressure oil in the pipeline, protecting the hydraulic control system and increasing the service life of the hydraulic control system.

[0054] Preferably, the pressure source control module also includes an oil return filter 2, and the oil return port of the first electro-hydraulic reversing valve 1101, the oil return port of the second electro-hydraulic reversing valve 1102, the oil return port of the third electro-hydraulic reversing valve 1103, the overflow port of the first overflow valve 101, the overflow port of the second overflow valve 102 and the overflow port of the third overflow valve 103 are all connected to the oil inlet of the oil return filter 2 after being merged through a pipeline, and the oil outlet of the oil return filter 2 is connected to the oil return port T of the pressure source control module.

[0055] Specifically, the oil return filter 2 is used to filter out impurities in all oil return pipelines, thereby protecting the hydraulic control system and increasing the service life of the hydraulic control system.

[0056] Preferably, the pressure source control module further comprises an electromagnetic overflow valve 7 , and the electromagnetic overflow valve 7 is connected to the main pipeline of the oil inlet of the return oil filter 2 .

[0057] Specifically, the electromagnetic relief valve 7 is used to prevent the output of the constant pressure variable pump 1 from being over-pressured.

[0058] Embodiment 2:

[0059] On the basis of Example 1, Figure 2 As shown, when the bimetallic composite pipe is compositely loaded, the first master hydraulic cylinder 1501 and the second master hydraulic cylinder 1502 make the composite pipe perform positive and reverse bending movements in the vertical direction through the first bending force hinge point B and the second bending force hinge point C. At the same time, the first axial hydraulic cylinder 1601 and the second axial hydraulic cylinder 1602 synchronously extend the piston rods to make the G point and the H point move inward, so that the AG lever rotates around the E point and the F point, thereby applying axial tension to the composite pipe at points A and D.

[0060] Since the radius of curvature of the composite pipe is constantly changing when it is bent in the forward and reverse directions, the displacements of points B and C are detected by the first displacement sensor 1401 and the second displacement sensor 1402. The axial tension change at point A can be obtained through theoretical calculation, and the system working pressure required by the first axial hydraulic cylinder 1601 and the second axial hydraulic cylinder 1602 can be inferred from the axial force.

[0061] The working pressure of the master hydraulic cylinder control module is greater than the working pressure of the axial hydraulic cylinder control module.

[0062] Embodiment 3:

[0063] On the basis of Example 2, in the present invention, in the cyclic bending state, the first electro-hydraulic reversing valve 1101, the first electromagnetic ball valve 1201, the second electromagnetic ball valve 1202, the third electromagnetic ball valve 1203, and the fourth electromagnetic ball valve 1204 are all energized, and the forward and reverse cyclic bending of the composite pipe is controlled by controlling the reversing of the first electro-hydraulic reversing valve 1101.

[0064] Embodiment 4:

[0065] On the basis of Example 3, in the composite loading state, the first electro-hydraulic reversing valve 1101, the first electromagnetic ball valve 1201, the second electromagnetic ball valve 1202, the third electromagnetic ball valve 1203, and the fourth electromagnetic ball valve 1204 are all powered, and the forward and reverse cyclic bending of the composite pipe is controlled by controlling the reversal of the first electro-hydraulic reversing valve 1101. At the same time, the proportional relief pressure reducing valve 9, the first electro-hydraulic reversing valve 1101, the second electro-hydraulic reversing valve 1102, the fifth electromagnetic ball valve 1205, and the sixth electromagnetic ball valve 1206 are powered, and the proportional relief pressure reducing valve 9 is controlled by closed-loop feedback to control the system pressure of the axial hydraulic cylinder control module.

[0066] Embodiment 5:

[0067] On the basis of Example 4, before the composite loading test, the first master hydraulic cylinder 1501 and the second master hydraulic cylinder 1502 need to be quickly moved to the mid-stroke position to maintain a horizontal state to place the composite pipe. At this time, the first electro-hydraulic reversing valve 1101, the first electromagnetic ball valve 1201, the second electromagnetic ball valve 1202, the third electromagnetic ball valve 1203, the fourth electromagnetic ball valve 1204, the seventh electromagnetic ball valve 1207, and the eighth electromagnetic ball valve 1208 are energized to realize differential connection, so that the first master hydraulic cylinder 1501 and the second master hydraulic cylinder 1502 are quickly extended to the specified position.

[0068] Embodiment 6:

[0069] On the basis of Example 5, in the emergency stop state of the present invention, all solenoid valves lose power, and the oil in the A and B chambers of the master hydraulic cylinders are locked in the chambers (the master hydraulic cylinders include the first master hydraulic cylinder 1501 and the second master hydraulic cylinder 1502, and the A and B chambers refer to the A1, B1, A2, and B2 chambers). At this time, the bimetallic composite pipe remains in its original state, and the oil in the A chamber of the axial hydraulic cylinder is locked in the chamber (the A3 chamber of the first axial hydraulic cylinder 1601 and the A4 chamber of the second axial hydraulic cylinder 1602), and the axial tension remains unchanged, that is, the bending and tensile forces remain unchanged, waiting for on-site troubleshooting.

[0070] The composite pipe four-point composite loading hydraulic control system of the present invention can also be applied to multi-point (≥4) bending and stretching conditions, and only requires configuring a corresponding number of master hydraulic cylinder valve control systems and increasing the flow rate of the pressure source.

[0071] In the description of the present invention, it is necessary to understand that the orientation or positional relationship indicated by terms such as “positive”, “upper”, and “lower” are based on the orientation or positional relationship shown in the drawings, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, the terms describing the positional relationship in the drawings are only used for illustrative purposes and cannot be understood as a limitation on the present invention.

[0072] The above examples are merely illustrative of the present invention and do not constitute a limitation on the protection scope of the present invention. All designs that are the same or similar to the present invention fall within the protection scope of the present invention.

Claims

1. A composite pipe four-point composite loading hydraulic control system, characterized in that: The invention comprises a main hydraulic cylinder control module, an axial hydraulic cylinder control module and a pressure source control module; the main hydraulic cylinder control module comprises a first main hydraulic cylinder (1501), a second main hydraulic cylinder (1502) and a first electro-hydraulic reversing valve (1101); the axial hydraulic cylinder control module comprises a first axial hydraulic cylinder (1601), a second axial hydraulic cylinder (1602), a second electro-hydraulic reversing valve (1102) and a third electro-hydraulic reversing valve (1103); the pressure oil port P of the pressure source control module is respectively connected to the oil inlet of the first electro-hydraulic reversing valve (1101), the oil inlet of the second electro-hydraulic reversing valve (1102) and the pressure oil port P of the pressure source control module. The oil inlet of the third electro-hydraulic reversing valve (1103) and the oil outlet of the first electro-hydraulic reversing valve (1101) are respectively connected to the first master hydraulic cylinder (1501) and the second master hydraulic cylinder (1502); the oil outlet of the second electro-hydraulic reversing valve (1102) is connected to the first axial hydraulic cylinder (1601); the oil outlet of the third electro-hydraulic reversing valve (1103) is connected to the second axial hydraulic cylinder (1602); and the oil return port of the first electro-hydraulic reversing valve (1101), the oil return port of the second electro-hydraulic reversing valve (1102) and the oil return port of the third electro-hydraulic reversing valve (1103) are all connected to the oil return port T of the pressure source control module.

2. The composite pipe four-point composite loading hydraulic control system according to claim 1, characterized in that: The master hydraulic cylinder control module further comprises a first overflow valve (101), and the axial hydraulic cylinder control module further comprises a second overflow valve (102) and a third overflow valve (103); the oil inlet of the first overflow valve (101) is connected to the oil outlet of the first electro-hydraulic reversing valve (1101), the oil outlet of the second electro-hydraulic reversing valve (1102) is connected to the rodless chamber A3 of the first axial hydraulic cylinder (1601) via the second overflow valve (102), and the oil outlet of the third electro-hydraulic reversing valve (1103) is connected to the rodless chamber A3 of the first axial hydraulic cylinder (1601) via the second overflow valve (102). The oil outlet of the pressure source control module (101) is connected to the rodless chamber A4 of the second axial hydraulic cylinder (1602) through the third overflow valve (103); the oil return port of the first electro-hydraulic reversing valve (1101), the oil return port of the second electro-hydraulic reversing valve (1102), the oil return port of the third electro-hydraulic reversing valve (1103), the overflow port of the first overflow valve (101), the overflow port of the second overflow valve (102) and the overflow port of the third overflow valve (103) are all connected to the oil return port T of the pressure source control module.

3. The composite pipe four-point composite loading hydraulic control system according to claim 2, characterized in that: The master hydraulic cylinder control module further comprises a first one-way speed regulating valve (1301), a second one-way speed regulating valve (1302), a third one-way speed regulating valve (1303) and a fourth one-way speed regulating valve (1304); one oil outlet of the first electro-hydraulic reversing valve (1101) is connected to the rodless chamber A1 of the first master hydraulic cylinder (1501) through the first one-way speed regulating valve (1301); two oil outlets of the first electro-hydraulic reversing valve (1101) are connected to the rodless chamber A1 of the first master hydraulic cylinder (1501) through the first one-way speed regulating valve (1301); The rod chamber B1 of the first master hydraulic cylinder (1501) is connected through the second one-way speed regulating valve (1302), the three-way oil outlet of the first electro-hydraulic reversing valve (1101) is connected to the rodless chamber A2 of the second master hydraulic cylinder (1502) through the third one-way speed regulating valve (1303), and the four-way oil outlet of the first electro-hydraulic reversing valve (1101) is connected to the rod chamber B2 of the second master hydraulic cylinder (1502) through the fourth one-way speed regulating valve (1304); The axial hydraulic cylinder control module also includes a fifth one-way speed regulating valve (1305), a sixth one-way speed regulating valve (1306), a seventh one-way speed regulating valve (1307) and an eighth one-way speed regulating valve (1308); one oil outlet of the second electro-hydraulic reversing valve (1102) is connected to the rodless chamber A3 of the first axial hydraulic cylinder (1601) through the second overflow valve (102) and the fifth one-way speed regulating valve (1305); two oil outlets of the second electro-hydraulic reversing valve (1102) are connected to the rod chamber B3 of the first axial hydraulic cylinder (1601) through the sixth one-way speed regulating valve (1306); One oil outlet of the third electro-hydraulic reversing valve (1103) is connected to the rodless chamber A4 of the second axial hydraulic cylinder (1602) through the third overflow valve (103) and the seventh one-way speed regulating valve (1307), and the second oil outlet of the third electro-hydraulic reversing valve (1103) is connected to the rod chamber B4 of the second axial hydraulic cylinder (1602) through the eighth one-way speed regulating valve (1308).

4. The composite pipe four-point composite loading hydraulic control system according to claim 3, characterized in that: The master hydraulic cylinder control module further comprises a first electromagnetic ball valve (1201), a second electromagnetic ball valve (1202), a third electromagnetic ball valve (1203) and a fourth electromagnetic ball valve (1204); the first electromagnetic ball valve (1201) is connected between the first one-way speed regulating valve (1301) and the first electro-hydraulic reversing valve (1101), the second electromagnetic ball valve (1202) is connected between the second one-way speed regulating valve (1302) and the first electro-hydraulic reversing valve (1101), the third electromagnetic ball valve (1203) is connected between the third one-way speed regulating valve (1303) and the first electro-hydraulic reversing valve (1101), and the fourth electromagnetic ball valve (1204) is connected between the fourth one-way speed regulating valve (1304) and the first electro-hydraulic reversing valve (1101); The axial hydraulic cylinder control module also includes a fifth electromagnetic ball valve (1205) and a sixth electromagnetic ball valve (1206), wherein the fifth electromagnetic ball valve (1205) is connected between the second overflow valve (102) and the second electro-hydraulic reversing valve (1102), and the sixth electromagnetic ball valve (1206) is connected between the third overflow valve (103) and the third electro-hydraulic reversing valve (1103).

5. The composite pipe four-point composite loading hydraulic control system according to claim 4, characterized in that: The master hydraulic cylinder control module also includes a seventh electromagnetic ball valve (1207), a ninth one-way speed regulating valve (1309), an eighth electromagnetic ball valve (1208) and a tenth one-way speed regulating valve (1310). The seventh electromagnetic ball valve (1207) and the ninth one-way speed regulating valve (1309) are connected in parallel between the rodless chamber A1 of the first master hydraulic cylinder (1501) and the rod chamber B1 of the first master hydraulic cylinder (1501). The eighth electromagnetic ball valve (1208) and the tenth one-way speed regulating valve (1310) are connected in parallel between the rodless chamber A2 of the second master hydraulic cylinder (1502) and the rod chamber B2 of the second master hydraulic cylinder (1502).

6. The composite pipe four-point composite loading hydraulic control system according to claim 5, characterized in that: The axial hydraulic cylinder control module also includes a proportional overflow pressure reducing valve (9), and the pressure oil port P of the pressure source control module is respectively connected to the oil inlet of the second electro-hydraulic reversing valve (1102) and the oil inlet of the third electro-hydraulic reversing valve (1103) through the proportional overflow pressure reducing valve (9).

7. The composite pipe four-point composite loading hydraulic control system according to claim 6, characterized in that: The axial hydraulic cylinder control module also includes a second pressure gauge (402) and a second pressure sensor (502), and the proportional relief pressure reducing valve (9) is connected to the oil inlet of the second electro-hydraulic reversing valve (1102) and the oil inlet of the third electro-hydraulic reversing valve (1103) respectively through the second pressure gauge (402) and the second pressure sensor (502).

8. The composite pipe four-point composite loading hydraulic control system according to claim 2, characterized in that: The pressure source control module comprises a constant pressure variable pump (1), a one-way valve (6) and a high-pressure oil filter (8); the pressure oil port of the pressure source control module passes through the constant pressure variable pump (1), the one-way valve (6) and the high-pressure oil filter (8) in sequence and is connected to the oil inlet of the first electro-hydraulic reversing valve (1101) and the oil inlet of the proportional overflow pressure reducing valve (9) respectively.

9. The composite pipe four-point composite loading hydraulic control system according to claim 8, characterized in that: The pressure source control module further comprises an oil return filter (2); the oil return port of the first electro-hydraulic reversing valve (1101), the oil return port of the second electro-hydraulic reversing valve (1102), the oil return port of the third electro-hydraulic reversing valve (1103), the overflow port of the first overflow valve (101), the overflow port of the second overflow valve (102) and the overflow port of the third overflow valve (103) are all connected to the oil inlet of the oil return filter (2) after being merged through a pipeline; and the oil outlet of the oil return filter (2) is connected to the oil return port T of the pressure source control module.

10. The composite pipe four-point composite loading hydraulic control system according to claim 9, characterized in that: The pressure source control module further comprises an electromagnetic overflow valve (7), and the electromagnetic overflow valve (7) is connected to the main pipeline of the oil inlet of the return oil filter (2).

Images