A heavy-duty valve actuator with redundant servo control

Abstract

A redundant servo-controlled heavy-duty valve actuator relates to the technical field of servo control valves. This is to solve the problem that the existing servo valve has a short service life and that when replacing it, the turbine needs to be stopped or the power reduced in order to replace and repair the servo valve, which seriously reduces the operating economy of the turbine generator set. The servo control valve actuator of this device adopts two sets of servo valve control circuits. When the servo valve in use is stuck or leaking, it can be switched to another set of servo valve circuits for control, and the faulty servo valve can be isolated and repaired or replaced online. At this time, the turbine does not need to be stopped or operated at reduced power, which can effectively improve the operating economy of the turbine. Since the actuator has a redundant servo circuit, one set of servo valve circuits can be used for daily control, and the other set of servo valve circuits can be used as a standby. The redundant circuits can be used periodically and alternately, thereby increasing the service life. The present invention is applicable to the field of steam turbine technology.

Description

Technical Field

[0001] The present invention relates to the technical field of servo control valves, and in particular to a redundant servo-controlled heavy-duty valve actuator. Background Art

[0002] Currently, steam valve actuators in steam turbine generator sets are controlled by servo valves, a key component in controlling the turbine's valves. However, due to operational issues such as leakage, sticking, and coil aging, servo valves typically require the turbine to be shut down or operated at reduced power, isolating the valve actuators, before servo valve replacement and repair can be performed, severely impacting the turbine's economical operation.

[0003] In summary, the existing servo valve has a short service life, and when replacing it, the turbine needs to be shut down or the power reduced in order to replace and repair the servo valve, which seriously reduces the operating economy of the turbine generator set. Summary of the Invention

[0004] The present invention proposes a heavy-duty valve actuator with redundant servo control to solve the problem that the existing servo valve has a short service life and needs to shut down the turbine or reduce the power when replacing the servo valve, which seriously reduces the operating economy of the turbine generator set.

[0005] A redundant servo-controlled heavy-duty valve actuator of the present invention comprises an oil cylinder 1, an integrated block 2, a stop valve 3, an OV1 oil inlet valve 5, an OV2 oil inlet valve 6, a filter 7, an exhaust pressure measuring joint 8, an oil guide block 9, an SV2 servo valve 10, an SV1 servo valve 11, a cartridge valve 12, an oil return check valve 13, a safety oil check valve 14, a CV1 check valve 15, a CV2 check valve 20, a test solenoid valve 25, a YC1 hydraulically controlled check valve 26, a YC2 hydraulically controlled check valve 27, a throttle 28, and a cover plate 29.

[0006] An integrated block 2 is provided on the side of the oil cylinder 1, a filter 7 is provided at one end of the back of the integrated block 2, a test solenoid valve 25 is provided in the middle of the upper surface of the integrated block 2, an SV2 servo valve 10 and an SV1 servo valve 11 are provided on one end of the upper surface of the integrated block 2 in sequence from top to bottom, an HP high-pressure oil inlet port 4, a DP pressure return oil port 23 and an OPC / AST safety oil port 24 are provided on the other end of the upper surface of the integrated block 2 in sequence from top to bottom, an OV1 oil inlet valve 5 and an OV2 oil inlet valve 6 are provided on the top of the upper surface of the integrated block 2 in sequence along the length direction, a stop valve 3, an oil return check valve 13 and a safety oil check valve 14 are provided on one side of the integrated block 2 in sequence from top to bottom, The other side of the manifold 2 is evenly provided with a CV1 check valve 15, a PA1 measuring point port 16, a PB1 measuring point port 17, a PB2 measuring point port 18, a PA2 measuring point port 19, a CV2 check valve 20, and a working chamber measuring point port 21. One end of the interior of the manifold 2 is provided with a YC1 hydraulically controlled check valve 26 and a YC2 hydraulically controlled check valve 27 in sequence from top to bottom, and the output end of the YC1 hydraulically controlled check valve 26 is connected to the input end of the throttle 28. A cartridge valve 12 is provided downstream of the YC1 hydraulically controlled check valve 26, and a cover plate 29 is provided on the outer surface of the output end of the cartridge valve 12. An exhaust pressure measuring joint 8 and an oil guide block 9 are provided in sequence along the width direction at the top end of the side of the oil cylinder 1.

[0007] Furthermore, a dust cover 22 is provided on the upper surface of the integrated block 2;

[0008] Furthermore, the OPC / AST safety oil port 24 on the integrated block 2 is connected to the input end of the safety oil check valve 14 through an oil pipe, the output end of the safety oil check valve 14 is connected to the input end of the test solenoid valve 25, the output end of the test solenoid valve 25 is connected to one end of the CV1 check valve 15, the other end of the CV1 check valve 15 is connected to the first input end of the SV2 servo valve 10, the output end of the SV2 servo valve 10 is connected to one end of the YC2 hydraulic control check valve 27, and the other end of the YC2 hydraulic control check valve 27 is connected. It is connected to one end of the YC1 hydraulically controlled one-way valve 26 through an oil pipe, the other end of the YC1 hydraulically controlled one-way valve 26 is connected to the input end of the SV1 servo valve 11 through an oil pipe, the No. 1 output end of the SV1 servo valve 11 is connected to one end of the CV2 one-way valve 20, the other end of the CV2 one-way valve 20 is connected to one end of the CV1 one-way valve 15, the connection between the CV1 one-way valve 15 and the output end of the test solenoid valve 25 is connected to one end of the return oil one-way valve 13, and the other end of the return oil one-way valve 13 is connected to the DP pressurized oil return port 2 through an oil pipe. 3, the second output end of the SV1 servo valve 11 is connected to one end of the OV1 oil inlet valve 5, the other end of the OV1 oil inlet valve 5 is connected to one end of the OV2 oil inlet valve 6, the other end of the OV2 oil inlet valve 6 is connected to the second output end of the SV2 servo valve 10, the other end of the OV1 oil inlet valve 5 and one end of the OV2 oil inlet valve 6 are connected to one end of the stop valve 3, and the other end of the stop valve 3 is connected to the HP high-pressure oil inlet 4 through the oil pipe, the output end of the test solenoid valve 25 is connected to one end of the CV1 one-way valve 15 The input end of the unloading valve is connected to the oil pipe, and the No. 1 output end of the unloading valve is connected to the oil delivery hole at the rodless chamber of the oil cylinder 1. The connection between the output end of the safety oil check valve 14 and the input end of the test solenoid valve 25 is connected to the No. 2 output end of the unloading valve through the oil pipe. The other end of the YC2 hydraulic control check valve 27 and the connection between one end of the YC1 hydraulic control check valve 26 and the blocking port of the unloading valve are connected to the oil pipe. The connection between one end of the YC1 hydraulic control check valve 26 and the blocking port of the unloading valve is connected to the oil delivery hole at the rod chamber of the oil cylinder 1 through the oil pipe.

[0009] Furthermore, the connection between the second output end of the SV1 servo valve 11 and one end of the OV1 oil inlet valve 5 is connected to the other end of the YC1 hydraulic control one-way valve 26 through an oil pipe, and a throttle is provided on the oil pipe;

[0010] Furthermore, the other end of the OV2 oil inlet valve 6 is connected to the second output end of the SV2 servo valve 10 through an oil pipe and connected to one end of the YC2 hydraulic control one-way valve 27, and a throttle is provided on the oil pipe;

[0011] Furthermore, the connection between one end of the OV2 oil inlet valve 6 and one end of the stop valve 3 is connected to the output end of the safety oil check valve 14 through an oil pipe;

[0012] Furthermore, the connection between the other end of the YC1 hydraulically controlled one-way valve 26 and the input end of the SV1 servo valve 11 is connected to the PB1 measuring point port 17 on the manifold block 2 through an oil pipe;

[0013] Furthermore, the connection between the second output terminal of the SV1 servo valve 11 and one end of the OV1 oil inlet valve 5 is connected to the PA1 measuring point port 16 on the manifold 2 through an oil pipe;

[0014] Furthermore, the connection between the output end of the SV2 servo valve 10 and one end of the YC2 hydraulically controlled one-way valve 27 is connected to the PB2 measuring point port 18 on the manifold block 2 through an oil pipe;

[0015] Furthermore, the connection between the other end of the OV2 oil inlet valve 6 and the second output end of the SV2 servo valve 10 is connected to the PA2 measuring point port 19 on the integrated block 2 through an oil pipe;

[0016] Furthermore, a displacement sensor is provided at the end of the telescopic rod of the oil cylinder 1;

[0017] Furthermore, when in use, the high-pressure oil comes out of the OV1 oil inlet valve 5 and flows to the output port of the SV1 servo valve 11 and the control port of the YC1 hydraulically controlled one-way valve 26 respectively. The output port of the SV1 servo valve 11 is connected to the forward inlet of the YC1 hydraulically controlled one-way valve 26. The forward outlet of the YC1 hydraulically controlled one-way valve 26 is connected to the working chamber of the oil cylinder 1. The T port of the SV1 servo valve 11 is connected to the DP pressurized return oil 23 through the one-way valve. When the OV1 oil inlet valve 5 is turned on, pressure exists at the control port of the YC1 hydraulically controlled one-way valve 26, and the YC1 hydraulically controlled one-way valve 26 allows bidirectional flow, so that the SV1 servo valve 11 can operate normally. When the OV1 oil inlet valve 5 is turned off, the pressure at the control port of the YC1 hydraulically controlled one-way valve 26 is released, and the YC1 hydraulically controlled one-way valve 26 can only flow in the forward direction. The oil inlet to the P port of the SV1 servo valve 11 is cut off by the OV1 oil inlet valve 5, and the return flow from the cylinder to the A port of the SV1 servo valve 11 is cut off by the YC1 hydraulically controlled one-way valve 26. The return flow from the pressurized return oil line to the T port of the SV1 servo valve 11 is cut off by the one-way valve CV1, thereby isolating the SV1 servo valve 11 and allowing the SV2 servo valve 10 to be replaced.

[0018] The specific steps for replacing the SV2 servo valve 10 are as follows:

[0019] Now unplug the SV2 servo valve 10 cable plug; close the No. 1 OV2 oil inlet valve 6; then observe the oil pressure at the PA2 measuring point port and the PB2 measuring point port 18, and remove the SV2 servo valve 10 after the oil pressure decreases and stabilizes; finally, open the OV2 oil inlet valve 6 after replacing the new servo valve; connect the cable plug of the SV2 servo valve 10.

[0020] Compared with the prior art, the present invention has the following beneficial effects:

[0021] The present invention overcomes the shortcomings of the prior art. The servo control valve actuator of this device adopts two sets of servo valve control circuits. When the servo valve in use is stuck or leaking, it can be switched to the other set of servo valve circuits for control, and the faulty servo valve can be isolated and repaired or replaced online. At this time, the turbine does not need to be shut down or run at reduced power, which can effectively improve the operating economy of the turbine. Since the actuator has redundant servo circuits, one set of servo valve circuits can be used for daily control, and the other set of servo valve circuits can be used as a backup. The redundant circuits can be used periodically and alternately, thereby increasing the service life. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] Figure 1 is a top view of a redundant servo-controlled heavy-duty valve actuator according to the present invention;

[0023] Figure 2 It is a left side view of a redundant servo-controlled heavy-duty valve actuator according to the present invention;

[0024] Figure 3 It is a right side view of a redundant servo-controlled heavy-duty valve actuator according to the present invention;

[0025] Figure 4 yes Figure 1 A cross-sectional view of the redundant servo-controlled heavy-duty valve actuator;

[0026] Figure 5 yes Figure 4 A side sectional view of the redundant servo-controlled heavy-duty valve actuator at position BB;

[0027] Figure 6 yes Figure 1 A cross-sectional view of CC of the redundant servo-controlled heavy-duty valve actuator;

[0028] Figure 7 This is a schematic diagram of the hydraulic oil circuit connections of a redundant servo-controlled heavy-duty valve actuator described in the present invention. DETAILED DESCRIPTION

[0029] Specific implementation method 1: Combination Figures 1 to 6 This embodiment is described as a redundant servo-controlled heavy-duty valve actuator, which comprises a cylinder 1, an integrated block 2, a stop valve 3, an OV1 oil inlet valve 5, an OV2 oil inlet valve 6, a filter 7, an exhaust pressure measuring joint 8, an oil guide block 9, an SV2 servo valve 10, an SV1 servo valve 11, a cartridge valve 12, an oil return check valve 13, a safety oil check valve 14, a CV1 check valve 15, a CV2 check valve 20, a test solenoid valve 25, a YC1 hydraulic control check valve 26, a YC2 hydraulic control check valve 27, a throttle 28, and a cover plate 29.

[0030] An integrated block 2 is provided on the side of the oil cylinder 1, a filter 7 is provided at one end of the back of the integrated block 2, a test solenoid valve 25 is provided in the middle of the upper surface of the integrated block 2, an SV2 servo valve 10 and an SV1 servo valve 11 are provided on one end of the upper surface of the integrated block 2 in sequence from top to bottom, an HP high-pressure oil inlet port 4, a DP pressure return oil port 23 and an OPC / AST safety oil port 24 are provided on the other end of the upper surface of the integrated block 2 in sequence from top to bottom, an OV1 oil inlet valve 5 and an OV2 oil inlet valve 6 are provided on the top of the upper surface of the integrated block 2 in sequence along the length direction, a stop valve 3, an oil return check valve 13 and a safety oil check valve 14 are provided on one side of the integrated block 2 in sequence from top to bottom, The other side of the manifold 2 is evenly provided with a CV1 check valve 15, a PA1 measuring point port 16, a PB1 measuring point port 17, a PB2 measuring point port 18, a PA2 measuring point port 19, a CV2 check valve 20, and a working chamber measuring point port 21. One end of the interior of the manifold 2 is provided with a YC1 hydraulically controlled check valve 26 and a YC2 hydraulically controlled check valve 27 in sequence from top to bottom, and the output end of the YC1 hydraulically controlled check valve 26 is connected to the input end of the throttle 28. A cartridge valve 12 is provided downstream of the YC1 hydraulically controlled check valve 26, and a cover plate 29 is provided on the outer surface of the output end of the cartridge valve 12. An exhaust pressure measuring joint 8 and an oil guide block 9 are provided in sequence along the width direction at the top end of the side of the oil cylinder 1.

[0031] In this specific embodiment, when in use, the high-pressure oil comes out of the OV1 oil inlet valve 5 and flows to the output port of the SV1 servo valve 11 and the control port of the YC1 hydraulically controlled one-way valve 26 respectively. The output port of the SV1 servo valve 11 is connected to the forward inlet of the YC1 hydraulically controlled one-way valve 26, and the forward outlet of the YC1 hydraulically controlled one-way valve 26 is connected to the working chamber of the oil cylinder 1. The T port of the SV1 servo valve 11 is connected to the DP pressurized return oil 23 through the one-way valve. When the OV1 oil inlet valve 5 is turned on, pressure exists at the control port of the YC1 hydraulically controlled one-way valve 26, and the YC1 hydraulically controlled one-way valve 26 allows bidirectional flow, so that the SV1 servo valve 11 can operate normally. When the OV1 oil inlet valve 5 is turned off, the pressure at the control port of the YC1 hydraulically controlled one-way valve 26 is released, and the YC1 hydraulically controlled one-way valve 26 can only flow in the forward direction. The oil inlet to the P port of the SV1 servo valve 11 is cut off by the OV1 oil inlet valve 5, and the return flow from the cylinder to the A port of the SV1 servo valve 11 is cut off by the YC1 hydraulically controlled one-way valve 26. The return flow from the pressurized return oil line to the T port of the SV1 servo valve 11 is cut off by the one-way valve CV1, thereby isolating the SV1 servo valve 11 and allowing the SV2 servo valve 10 to be replaced.

[0032] The specific steps for replacing the SV2 servo valve 10 are as follows:

[0033] Now unplug the SV2 servo valve 10 cable plug; close the No. 1 OV2 oil inlet valve 6; then observe the oil pressure at the PA2 measuring point port and the PB2 measuring point port 18, and remove the SV2 servo valve 10 after the oil pressure decreases and stabilizes; finally, open the OV2 oil inlet valve 6 after replacing the new servo valve; connect the cable plug of the SV2 servo valve 10.

[0034] Specific implementation method 2: Combination Figure 3 This embodiment is described as a further limitation of the valve actuator described in the first embodiment. In this embodiment, a heavy-duty valve actuator with redundant servo control is described, in which a dust cover 22 is provided on the upper surface of the manifold block 2.

[0035] In this specific embodiment, a dust cover 22 is provided on the upper surface of the integrated block 2 to improve the dust removal function.

[0036] Specific implementation method three: Combination Figures 1 to 7This embodiment is described. This embodiment is a further limitation of the valve actuator described in the specific embodiment 1. In this embodiment, a redundant servo-controlled heavy-duty valve actuator is described. The OPC / AST safety oil port 24 on the manifold block 2 is connected to the input end of the safety oil check valve 14 through an oil pipe. The output end of the safety oil check valve 14 is connected to the input end of the test solenoid valve 25. The output end of the test solenoid valve 25 is connected to one end of the CV1 check valve 15. The other end of the CV1 check valve 15 is connected to the first input end of the SV2 servo valve 10. Then, the output end of the SV2 servo valve 10 is connected to one end of the YC2 hydraulic control one-way valve 27, the other end of the YC2 hydraulic control one-way valve 27 is connected to one end of the YC1 hydraulic control one-way valve 26 through an oil pipe, the other end of the YC1 hydraulic control one-way valve 26 is connected to the input end of the SV1 servo valve 11 through an oil pipe, the No. 1 output end of the SV1 servo valve 11 is connected to one end of the CV2 one-way valve 20, the other end of the CV2 one-way valve 20 is connected to one end of the CV1 one-way valve 15, and the connection between the CV1 one-way valve 15 and the output end of the test solenoid valve 25 is connected to the return oil one-way valve 13 The other end of the return oil check valve 13 is connected to the DP pressure return oil port 23 through an oil pipe. The second output end of the SV1 servo valve 11 is connected to one end of the OV1 oil inlet valve 5. The other end of the OV1 oil inlet valve 5 is connected to one end of the OV2 oil inlet valve 6. The other end of the OV2 oil inlet valve 6 is connected to the second output end of the SV2 servo valve 10. The connection between the other end of the OV1 oil inlet valve 5 and one end of the OV2 oil inlet valve 6 is connected to one end of the stop valve 3, and the other end of the stop valve 3 is connected to the HP high-pressure oil inlet port 4 through an oil pipe. The output end of the test solenoid valve 25 The connection point with one end of the CV1 one-way valve 15 is connected to the input end of the unloading valve through an oil pipe, and the No. 1 output end of the unloading valve is connected to the oil delivery hole at the rodless chamber of the oil cylinder 1. The connection point between the output end of the safety oil one-way valve 14 and the input end of the test solenoid valve 25 is connected to the No. 2 output end of the unloading valve through an oil pipe. The connection point between the other end of the YC2 hydraulically controlled one-way valve 27 and one end of the YC1 hydraulically controlled one-way valve 26 is connected to the blocking port of the unloading valve through an oil pipe. The connection point between one end of the YC1 hydraulically controlled one-way valve 26 and the blocking port of the unloading valve is connected to the oil delivery hole at the rod chamber of the oil cylinder 1 through an oil pipe.

[0037] This specific implementation method uses two sets of servo valve control circuits. When the servo valve in use becomes stuck or leaks, it can be switched to another set of servo valve circuits for control, and the faulty servo valve can be isolated and repaired or replaced online. At this time, the turbine does not need to be shut down or run at reduced power, which can effectively improve the operating economy of the turbine.

[0038] Specific implementation method four: Combination Figures 1 to 7This embodiment is described as a further limitation of the valve actuator described in the third embodiment. This embodiment describes a redundant servo-controlled heavy-duty valve actuator, in which the second output end of the SV1 servo valve 11 and one end of the OV1 oil inlet valve 5 are connected to the other end of the YC1 hydraulically controlled one-way valve 26 through an oil pipe, and a throttle is provided on the oil pipe.

[0039] Specific implementation method five: Combination Figures 1 to 7 This embodiment is described as a further limitation of the valve actuator described in the third embodiment. This embodiment describes a redundant servo-controlled heavy-duty valve actuator, in which the other end of the OV2 oil inlet valve 6 is connected to the second output end of the SV2 servo valve 10 through an oil pipe and one end of the YC2 hydraulically controlled one-way valve 27, and a throttle is provided on the oil pipe.

[0040] Specific implementation method six: combination Figures 1 to 7 This embodiment is described as a further limitation of the valve actuator described in the third embodiment. This embodiment describes a redundant servo-controlled heavy-duty valve actuator, in which one end of the OV2 oil inlet valve 6 and one end of the shut-off valve 3 are connected to the output end of the safety oil one-way valve 14 through an oil pipe.

[0041] Specific implementation method seven: combination Figures 1 to 7 This embodiment is described as a further limitation of the valve actuator described in the third embodiment. This embodiment describes a redundant servo-controlled heavy-duty valve actuator, in which the other end of the YC1 hydraulically controlled one-way valve 26 is connected to the input end of the SV1 servo valve 11 through an oil pipe and the PB1 measuring point port 17 on the integrated block 2.

[0042] Specific implementation method eight: combination Figures 1 to 7 This embodiment is described as a further limitation of the valve actuator described in the third embodiment. This embodiment describes a redundant servo-controlled heavy-duty valve actuator, in which the second output end of the SV1 servo valve 11 and one end of the OV1 oil inlet valve 5 are connected to the PA1 measuring point port 16 on the integrated block 2 through an oil pipe.

[0043] Specific implementation method nine: combination Figures 1 to 7 This embodiment is described as a further limitation of the valve actuator described in the third embodiment. This embodiment describes a redundant servo-controlled heavy-duty valve actuator, in which the connection between the output end of the SV2 servo valve 10 and one end of the YC2 hydraulically controlled one-way valve 27 is connected to the PB2 measuring point port 18 on the integrated block 2 through an oil pipe.

[0044] Specific implementation method ten: Combination Figures 1 to 7 To explain this embodiment, this embodiment is a further limitation of the valve actuator described in the third specific embodiment. This embodiment describes a redundant servo-controlled heavy-duty valve actuator, in which the other end of the OV2 oil inlet valve 6 is connected to the second output end of the SV2 servo valve 10 through an oil pipe and the PA2 measuring point port 19 on the integrated block 2; a displacement sensor is provided at the end of the telescopic rod of the oil cylinder 1.

[0045] How it works

[0046] During use, high-pressure oil comes out of the OV1 oil inlet valve 5 and flows to the output port of the SV1 servo valve 11 and the control port of the YC1 hydraulically controlled one-way valve 26 respectively. The output port of the SV1 servo valve 11 is connected to the forward inlet of the YC1 hydraulically controlled one-way valve 26, and the forward outlet of the YC1 hydraulically controlled one-way valve 26 is connected to the working chamber of the cylinder 1. The T port of the SV1 servo valve 11 is connected to the DP pressurized return oil 23 through the one-way valve. When the OV1 oil inlet valve 5 is turned on, pressure exists at the control port of the YC1 hydraulically controlled one-way valve 26, and the YC1 hydraulically controlled one-way valve 26 allows bidirectional flow, so that the SV1 servo valve 11 can operate normally. When the OV1 oil inlet valve 5 is turned off, the pressure at the control port of the YC1 hydraulically controlled one-way valve 26 is released, and the YC1 hydraulically controlled one-way valve 26 can only flow in the forward direction. The oil inlet to the P port of the SV1 servo valve 11 is cut off by the OV1 oil inlet valve 5, and the return flow from the cylinder to the A port of the SV1 servo valve 11 is cut off by the YC1 hydraulically controlled one-way valve 26. The return flow from the pressurized return oil line to the T port of the SV1 servo valve 11 is cut off by the one-way valve CV1, thereby isolating the SV1 servo valve 11 and allowing the SV2 servo valve 10 to be replaced.

[0047] The specific steps for replacing the SV2 servo valve 10 are as follows:

[0048] Now unplug the SV2 servo valve 10 cable plug; close the No. 1 OV2 oil inlet valve 6; then observe the oil pressure at the PA2 measuring point port and the PB2 measuring point port 18, and remove the SV2 servo valve 10 after the oil pressure decreases and stabilizes; finally, open the OV2 oil inlet valve 6 after replacing the new servo valve; connect the cable plug of the SV2 servo valve 10.

Claims

1. A redundant servo-controlled heavy-duty valve actuator, characterized by: It includes an oil cylinder (1), an integrated block (2), a stop valve (3), an OV1 oil inlet valve (5), an OV2 oil inlet valve (6), a filter (7), an exhaust pressure measuring joint (8), an oil guide block (9), an SV2 servo valve (10), an SV1 servo valve (11), a cartridge valve (12), an oil return check valve (13), a safety oil check valve (14), a CV1 check valve (15), a CV2 check valve (20), a test solenoid valve (25), a YC1 hydraulic control check valve (26), a YC2 hydraulic control check valve (27), a throttle (28) and a cover plate (29); An integrated block (2) is provided on the side of the oil cylinder (1), a filter (7) is provided at one end of the back of the integrated block (2), a test solenoid valve (25) is provided in the middle of the upper surface of the integrated block (2), an SV2 servo valve (10) and an SV1 servo valve (11) are provided on one end of the upper surface of the integrated block (2) in sequence from top to bottom, an HP high-pressure oil inlet (4), a DP pressure return oil port (23) and an OPC / AST safety oil port (24) are provided on the other end of the upper surface of the integrated block (2) in sequence from top to bottom, an OV1 oil inlet valve (5) and an OV2 oil inlet valve (6) are provided on the top of the upper surface of the integrated block (2) in sequence along the length direction, a stop valve (3), a return oil check valve (13) and a safety oil check valve (14) are provided on one side of the integrated block (2) in sequence from top to bottom, and the integrated block (2) is provided with a plurality of oil pumps, a plurality of oil pumps and a plurality of oil pumps. The other side of the integrated block (2) is evenly provided with a CV1 one-way valve (15), a PA1 measuring point port (16), a PB1 measuring point port (17), a PB2 measuring point port (18), a PA2 measuring point port (19), a CV2 one-way valve (20) and a working chamber measuring point port (21). One end of the interior of the integrated block (2) is provided with a YC1 hydraulically controlled one-way valve (26) and a YC2 hydraulically controlled one-way valve (27) in sequence from top to bottom, and the output end of the YC1 hydraulically controlled one-way valve (26) is connected to the input end of the throttle (28). A cartridge valve (12) is provided downstream of the YC1 hydraulically controlled one-way valve (26), and a cover plate (29) is provided on the outer surface of the output end of the cartridge valve (12). An exhaust pressure measuring joint (8) and an oil guide block (9) are provided in sequence along the width direction at the top end of the side of the oil cylinder (1).

2. The redundant servo-controlled heavy-duty valve actuator according to claim 1, characterized in that: The upper surface of the integrated block (2) is provided with a dust cover (22).

3. The redundant servo-controlled heavy-duty valve actuator according to claim 1, characterized in that: The OPC / AST safety oil port (24) on the manifold (2) is connected to the input end of the safety oil check valve (14) through an oil pipe, the output end of the safety oil check valve (14) is connected to the input end of the test solenoid valve (25), the output end of the test solenoid valve (25) is connected to one end of the CV1 check valve (15), the other end of the CV1 check valve (15) is connected to the first input end of the SV2 servo valve (10), the output end of the SV2 servo valve (10) is connected to one end of the YC2 hydraulic control check valve (27), the other end of the YC2 hydraulic control check valve (27) is connected through The oil pipe is connected to one end of the YC1 hydraulic control one-way valve (26), the other end of the YC1 hydraulic control one-way valve (26) is connected to the input end of the SV1 servo valve (11) through the oil pipe, the No. 1 output end of the SV1 servo valve (11) is connected to one end of the CV2 one-way valve (20), the other end of the CV2 one-way valve (20) is connected to one end of the CV1 one-way valve (15), the connection between the CV1 one-way valve (15) and the output end of the test solenoid valve (25) is connected to one end of the return oil one-way valve (13), the other end of the return oil one-way valve (13) is connected to the DP pressure return oil port (20) through the oil pipe. 3), the second output end of the SV1 servo valve (11) is connected to one end of the OV1 oil inlet valve (5), the other end of the OV1 oil inlet valve (5) is connected to one end of the OV2 oil inlet valve (6), the other end of the OV2 oil inlet valve (6) is connected to the second output end of the SV2 servo valve (10), the connection between the other end of the OV1 oil inlet valve (5) and one end of the OV2 oil inlet valve (6) is connected to one end of the stop valve (3), and the other end of the stop valve (3) is connected to the HP high-pressure oil inlet port (4) through the oil pipe, the output end of the test solenoid valve (25) is connected to the CV1 one-way valve (15) One end connection of the unloading valve is connected to the input end of the unloading valve through an oil pipe, and the No. 1 output end of the unloading valve is connected to the oil delivery hole at the rodless chamber of the oil cylinder (1). The output end of the safety oil one-way valve (14) and the input end connection of the test solenoid valve (25) are connected to the No. 2 output end of the unloading valve through an oil pipe. The other end of the YC2 hydraulic control one-way valve (27) and one end connection of the YC1 hydraulic control one-way valve (26) are connected to the blocking port of the unloading valve through an oil pipe. The connection of one end of the YC1 hydraulic control one-way valve (26) and the blocking port of the unloading valve are connected to the oil delivery hole at the rod chamber of the oil cylinder (1) through an oil pipe.

4. The redundant servo-controlled heavy-duty valve actuator according to claim 3, characterized in that: The connection between the second output end of the SV1 servo valve (11) and one end of the OV1 oil inlet valve (5) is connected to the other end of the YC1 hydraulic control one-way valve (26) through an oil pipe, and a throttle is provided on the oil pipe.

5. The redundant servo-controlled heavy-duty valve actuator according to claim 3, characterized in that: The other end of the OV2 oil inlet valve (6) is connected to the second output end of the SV2 servo valve (10) through an oil pipe and connected to one end of the YC2 hydraulic control one-way valve (27), and a throttle is provided on the oil pipe.

6. The redundant servo-controlled heavy-duty valve actuator according to claim 3, characterized in that: The connection between one end of the OV2 oil inlet valve (6) and one end of the stop valve (3) is connected to the output end of the safety oil one-way valve (14) through an oil pipe.

7. The redundant servo-controlled heavy-duty valve actuator according to claim 3, characterized in that: The connection between the other end of the YC1 hydraulically controlled one-way valve (26) and the input end of the SV1 servo valve (11) is connected to the PB1 measuring point port (17) on the integrated block (2) through an oil pipe.

8. The redundant servo-controlled heavy-duty valve actuator according to claim 3, characterized in that: The connection between the second output end of the SV1 servo valve (11) and one end of the OV1 oil inlet valve (5) is connected to the PA1 measuring point port (16) on the integrated block (2) through an oil pipe.

9. The redundant servo-controlled heavy-duty valve actuator according to claim 3, characterized in that: The connection between the output end of the SV2 servo valve (10) and one end of the YC2 hydraulic control one-way valve (27) is connected to the PB2 measuring point port (18) on the integrated block (2) through an oil pipe.

10. The redundant servo-controlled heavy-duty valve actuator according to claim 3, characterized in that: The connection between the other end of the OV2 oil inlet valve (6) and the second output end of the SV2 servo valve (10) is connected to the PA2 measuring point port (19) on the integrated block (2) through an oil pipe; and a displacement sensor is provided at the end of the telescopic rod of the oil cylinder (1).

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