Seismic source system, control method and control device thereof, storage medium and electronic equipment

Abstract

The invention belongs to the technical field of controllable seismic sources, and particularly provides a seismic source system and a control method and device thereof, a storage medium and electronic equipment, and the seismic source system comprises a liquid source, a vibration execution part, a first servo valve, a second servo valve and a control assembly. The vibration execution part comprises a first hydraulic cavity and a second hydraulic cavity; the first servo valve comprises a first control port, a first liquid inlet and a first liquid outlet, the first liquid inlet is communicated with a liquid source, and the first liquid outlet is communicated with the first hydraulic cavity; the second servo valve comprises a second control port, a second liquid inlet and a second liquid outlet, the second liquid inlet is communicated with the liquid source, and the second liquid outlet is communicated with the second hydraulic cavity; the control assembly is electrically connected with the first control port and the second control port, and the control assembly is used for controlling the opening degree of the first servo valve and the opening degree of the second servo valve. A double-valve-body structure is adopted, the odd harmonic distortion degree is reduced, the deep geological structure recognition precision is improved, and technical support is provided for high-resolution oil and gas reservoir exploration.

Description

Technical Field

[0001] This invention belongs to the field of controllable seismic source technology, and specifically relates to a seismic source system and its control method, control device, storage medium and electronic equipment. Background Technology

[0002] In related technologies, the source system, as a key piece of equipment in geophysical exploration, directly determines the accuracy of seismic data through the quality of its output force waveform. Currently, traditional source systems generally adopt an electro-hydraulic control architecture with a single servo valve. There is an inherent nonlinear relationship between the flow rate of the servo valve and the load pressure difference. During operation, especially under high load conditions, the source system will generate significant harmonic distortion, which severely degrades the signal-to-noise ratio and fidelity of the output signal, thereby affecting the ability to identify deep geological structures. Summary of the Invention

[0003] In a first aspect, embodiments of the present invention provide a vibration source system, the vibration source system including a liquid source, a vibration actuator, a first servo valve, a second servo valve, and a control component; the vibration actuator includes a first hydraulic chamber and a second hydraulic chamber; the first servo valve includes a first control port, a first liquid inlet, and a first liquid outlet, the first liquid inlet being connected to the liquid source, and the first liquid outlet being connected to the first hydraulic chamber; the second servo valve includes a second control port, a second liquid inlet, and a second liquid outlet, the second liquid inlet being connected to the liquid source, and the second liquid outlet being connected to the second hydraulic chamber; the control component is electrically connected to the first control port and the second control port, and the control component is used to control the opening degree of the first servo valve and the second servo valve.

[0004] In a second aspect, embodiments of the present invention provide a control method for a seismic source system, used in the seismic source system of the first aspect. The control method for the seismic source system includes: acquiring seismic source exploration requirements; generating a first driving signal and a second driving signal according to the seismic source exploration requirements; controlling the opening degree of a first servo valve according to the first driving signal; and controlling the opening degree of a second servo valve according to the second driving signal.

[0005] Thirdly, embodiments of the present invention provide a control device for a seismic source system, used in the seismic source system as described in the first aspect. The control device for the seismic source system includes a first processing unit, a second processing unit, and a control unit. The first processing unit is used to acquire seismic source exploration requirements; the second processing unit is used to generate a first driving signal and a second driving signal according to the seismic source exploration requirements; the control unit is used to control the opening degree of a first servo valve according to the first driving signal and to control the opening degree of a second servo valve according to the second driving signal.

[0006] Fourthly, embodiments of the present invention provide a storage medium storing a computer program thereon, wherein the computer program, when executed by a processor, implements the steps of the control method for the source system of the second aspect.

[0007] Fifthly, the present invention provides an electronic device, including a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor executes the computer program to implement the steps of the control method for the source system of the second aspect.

[0008] The beneficial effects of this invention are as follows: As can be seen from the above scheme, the vibration source system proposed in this invention includes a hydraulic source, a vibration actuator, a first servo valve, a second servo valve, and control components. The hydraulic source is the fluid supply part of the vibration source system, used to provide a continuous and stable supply of hydraulic oil. The vibration actuator is the power output part of the vibration source system, and its interior contains two independent first hydraulic chambers and second hydraulic chambers. The first hydraulic chamber is the upper chamber of the vibration actuator, and the second hydraulic chamber is the lower chamber of the vibration actuator.

[0009] The first servo valve is one of the core control components of the vibration source system. It includes a first control port, a first inlet, and a first outlet. The first control port receives electrical control signals, the first inlet is connected to a liquid source to obtain hydraulic oil, and the first outlet is connected to the first hydraulic chamber of the vibration actuator to deliver hydraulic oil. The second servo valve is another control component arranged in parallel with the first servo valve. It includes a second control port, a second inlet, and a second outlet. The second control port receives electrical control signals, the second inlet is connected to a liquid source, and the second outlet is connected to the second hydraulic chamber of the vibration actuator.

[0010] The control component is the control center of the seismic source system. It is connected to the first control port of the first servo valve and the second control port of the second servo valve via electrical connection. The control component can adjust the opening of the two servo valves through the first and second control ports.

[0011] In the vibration source system proposed in this invention, during operation, the control component simultaneously sends control signals to two servo valves. Specifically, it can send two synchronous control signals: one to the first control port of the first servo valve and the other to the second control port of the second servo valve. The control component adjusts the opening of the first and second servo valves. By adjusting the opening of the two servo valves, it controls the flow rate and pressure of hydraulic oil from the fluid source to the two hydraulic chambers of the vibration actuator, thereby driving the vibration actuator to generate the required vibration output. This invention, by using parallel dual valves to share the load, significantly reduces the actual working pressure difference of a single servo valve, ensuring that it always operates within the linear range of the flow-pressure characteristics, thus suppressing the generation of harmonic distortion at its source.

[0012] In summary, the seismic source system proposed in this invention, through its dual-valve structure of a first servo valve and a second servo valve, effectively avoids the nonlinear distortion problem under high-flow conditions with a single valve, significantly reducing the total harmonic distortion of the output force waveform. The signal-to-noise ratio and waveform fidelity of the seismic source system's output signal are fundamentally improved, particularly the phase consistency in the low-frequency and high-frequency bands, providing reliable data support for high-resolution oil and gas exploration. Under the same hydraulic power consumption, the seismic source system achieves a higher effective fundamental wave output force, improved energy utilization, and increased detection depth. This invention achieves performance breakthroughs through structural innovation, avoiding the safety risks associated with relying solely on ultra-high working pressure, and simultaneously enhancing system reliability and safety. Attached Figure Description

[0013] Figure 1 This is a schematic diagram illustrating the structure of a seismic source system according to an embodiment of the present invention; Figure 2 This graph shows the flow-pressure curve of a single servo valve in the seismic source system. Figure 3 This is a flow-pressure curve representing the load pressure of a single servo valve from 10% to 60%. Figure 4 This is one of the test data graphs for a certain type of controllable seismic source with a single servo valve performing equal-frequency scanning of a load in related technologies. Figure 5 This is one of the test data graphs for a certain type of controllable seismic source with a single servo valve performing equal-frequency scanning of a load in related technologies. Figure 6 The third figure shows the test data of a certain type of controllable seismic source with a single servo valve scanning a load at the same frequency in the relevant technology. Figure 7 This is one of the test data graphs showing a certain type of controllable seismic source with a single servo valve performing equal-frequency scanning of another load in related technologies; Figure 8 The second figure shows the test data of a certain type of controllable seismic source with a single servo valve performing equal-frequency scanning of another load in related technologies. Figure 9 The third figure shows the test data of a certain type of controllable seismic source with a single servo valve performing equal-frequency scanning of another load in related technologies. Figure 10 This indicates the relationship between displacement and distortion of a single servo valve in a seismic source system in related technologies; Figure 11 This graph shows the frequency response curves of two servo valves. Figure 12 A graph showing the absolute peak force of two servo valves; Figure 13 A graph showing the phase hysteresis curves of two servo valves; Figure 14 A diagram showing the servo valve displacement signals of two servo valves; Figure 15 A graph showing the fundamental force curves of two servo valves; Figure 16 This is a graph showing the harmonic distortion curves of two servo valves.

[0014] Figure 17 One of the flowcharts illustrating a control method for a seismic source system according to an embodiment of the present invention; Figure 18 A second schematic flowchart illustrating a control method for a seismic source system according to an embodiment of the present invention; Figure 19 A schematic block diagram illustrating the structure of a control device for a seismic source system according to an embodiment of the present invention; Figure 20 This is a schematic block diagram illustrating the structure of an electronic device according to an embodiment of the present invention.

[0015] Figure 1 In the diagram, 100 represents the vibration source system, 110 the vibration actuator, 112 the counterweight, 114 the first hydraulic chamber, 116 the second hydraulic chamber, 118 the piston, 120 the piston rod, 122 the plate, 130 the first servo valve, 132 the first control port, 134 the first motor, 136 the first valve core, 138 the first valve chamber, 140 the second servo valve, 142 the second control port, 144 the second motor, and 146 the second valve core. 48 is the second valve chamber, 150 is the control component, 152 is the controller, 154 is the junction box, 155 is the first interface, 156 is the second interface, 157 is the third interface, 158 is the fourth interface, 160 is the fifth interface, 162 is the sixth interface, 164 is the seventh interface, 170 is the first displacement sensor, 172 is the first acceleration sensor, 178 is the second acceleration sensor, 180 is the second displacement sensor, and 182 is the third displacement sensor. Detailed Implementation

[0016] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of the embodiments of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this invention. Based on the embodiments of this invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this invention.

[0017] like Figure 1As shown, in some embodiments of the present invention, a vibration source system 100 is proposed, including a liquid source, a vibration actuator 110, a first servo valve 130, a second servo valve 140, and a control component 150; the vibration actuator 110 includes a first hydraulic chamber 114 and a second hydraulic chamber 116; the first servo valve 130 includes a first control port 132, a first liquid inlet, and a first liquid outlet, the first liquid inlet being connected to the liquid source, and the first liquid outlet being connected to the first hydraulic chamber 114; the second servo valve 140 includes a second control port 142, a second liquid inlet, and a second liquid outlet, the second liquid inlet being connected to the liquid source, and the second liquid outlet being connected to the second hydraulic chamber 116; the control component 150 is electrically connected to the first control port 132 and the second control port 142, and the control component 150 is used to control the opening degree of the first servo valve 130 and the second servo valve 140.

[0018] In this embodiment, the vibration source system 100 proposed in this invention includes a hydraulic source, a vibration actuator 110, a first servo valve 130, a second servo valve 140, and a control component 150. The hydraulic source is the working fluid supply component of the system, used to provide a continuous and stable supply of hydraulic oil. Specifically, the hydraulic source includes a hydraulic oil tank, a pump unit, and an oil supply pipeline. The hydraulic oil tank serves as a medium storage container, and its interior is equipped with baffles and a multi-stage filtration device. The pump unit is connected to both the hydraulic oil tank and the oil supply pipeline, enabling the pumping of liquid from the hydraulic oil tank to the oil supply pipeline. Both the first and second inlets are connected to the hydraulic pipeline.

[0019] Specifically, the oil supply pipeline can be a single pipeline or a dual pipeline. The hydraulic oil tank is connected to the first inlet of the first servo valve 130 and the second inlet of the second servo valve 140 through two independent oil supply pipelines.

[0020] Specifically, a first sealing ring can be installed at the connection between the oil supply pipeline and the first liquid inlet, and a second sealing ring can be installed at the connection between the oil supply pipeline and the second liquid inlet.

[0021] Specifically, the liquid source can also be just an oil supply pipe connected to an external liquid supply device.

[0022] The vibration actuator 110 is the power output component of the seismic source system 100. The vibration actuator 110 internally contains two independent hydraulic chambers: a first hydraulic chamber 114 and a second hydraulic chamber 116. The first hydraulic chamber 114 is specifically the upper chamber of the vibration actuator 110, and the second hydraulic chamber 116 is specifically the lower chamber of the vibration actuator 110. The vibration actuator 110 converts the received hydraulic power into mechanical impact force, generating vibration and outputting seismic waves to the ground.

[0023] The first servo valve 130 is one of the core control components of the vibration source system 100. It includes a first control port 132, a first inlet, and a first outlet. The first control port 132 receives electrical control signals, the first inlet is connected to a liquid source to obtain hydraulic oil, and the first outlet is connected to the first hydraulic chamber 114 of the vibration actuator 110 to deliver hydraulic oil. The second servo valve 140 is another control component arranged in parallel with the first servo valve 130. The second servo valve 140 includes a second control port 142, a second inlet, and a second outlet. The second control port 142 receives electrical control signals, the second inlet is connected to a liquid source, and the second outlet is connected to the second hydraulic chamber 116 of the vibration actuator 110.

[0024] The control component 150 is the control center of the seismic source system 100. It is connected to the first control port 132 of the first servo valve 130 and the second control port 142 of the second servo valve 140 via electrical connection. The control component 150 can adjust the opening of the two servo valves through the first control port 132 and the second control port 142.

[0025] In the operation of the vibration source system 100 proposed in this invention, the control component 150 simultaneously sends control signals to two servo valves. By synchronously adjusting the opening degree of each servo valve, hydraulic oil is controlled to alternately enter the two hydraulic chambers of the vibration actuator 110: when high-pressure oil enters the first hydraulic chamber 114, low-pressure oil is discharged from the second hydraulic chamber 116; when high-pressure oil enters the second hydraulic chamber 116, low-pressure oil is discharged from the first hydraulic chamber 114. This drives the vibration actuator 110 to achieve reciprocating motion and generate the required vibration output. This invention, through parallel control of dual valves and alternating oil supply, significantly reduces the actual working pressure difference of a single servo valve, ensuring that it always operates within the linear range of the flow-pressure characteristics, thus suppressing the generation of harmonic distortion at its source.

[0026] The seismic source system 100 proposed in this invention, through a dual-valve structure of a first servo valve 130 and a second servo valve 140, effectively avoids the nonlinear distortion problem under high-flow conditions with a single valve, significantly reducing the total harmonic distortion of the output force waveform. The signal-to-noise ratio and waveform fidelity of the output signal of the seismic source system 100 are fundamentally improved, especially the phase consistency in the low-frequency and high-frequency bands is greatly enhanced, providing reliable data support for high-resolution oil and gas exploration. Under the same hydraulic power consumption, the seismic source system 100 has a higher effective fundamental wave output force, improved energy utilization, and increased detection depth. This invention achieves a performance breakthrough through structural innovation, avoiding the safety risks associated with relying solely on ultra-high working pressure, and simultaneously enhancing system reliability and safety.

[0027] Specifically, the control component 150 can send two synchronous control signals to control the first servo valve 130 and the second servo valve 140 respectively. The control component 150 generates a primary control current signal as a reference and sends it to the first servo valve 130, and generates a compensation control current signal that is synchronized with the primary control current signal in real time and sends it to the second servo valve 140.

[0028] like Figure 1 As shown, in some embodiments of the present invention, optionally, the first servo valve 130 further includes a first motor 134 and a first valve core 136, wherein the first motor 134 is electrically connected to the first control port 132; the first valve core 136 is disposed in the first valve chamber 138 of the first servo valve 130 and is located between the first inlet and the first outlet; the first valve core 136 is connected to the first motor 134, and the first motor 134 can drive the first valve core 136 to move under the control of the first control port 132, so as to change the opening degree of the first servo valve 130.

[0029] In this embodiment, for the internal actuator of the first servo valve 130, the present invention provides that the first servo valve 130 includes a first motor 134 and a first valve core 136. The first motor 134 acts as an electro-mechanical converter and is electrically connected to a first control port 132 for receiving electrical signals from the control component 150. Specifically, the control terminal of the first motor 134 is electrically connected to the first control port 132 for receiving weak current signals from the control component 150.

[0030] The first valve core 136 is installed in the first valve chamber 138 of the first servo valve 130. The axial position of the first valve core 136 directly controls the flow area between the first inlet and the first outlet. The first valve core 136 is connected to the first motor 134, so that the first motor 134 generates a corresponding torque or displacement after receiving an electrical signal, thereby driving the first valve core 136 to move. By changing the displacement of the first valve core 136, the opening of the first servo valve 130 can be precisely adjusted, thereby controlling the flow rate of hydraulic oil from the liquid source to the first hydraulic chamber 114. This invention achieves precise linear control of hydraulic flow rate by electrical signals through the design of the first servo valve 130.

[0031] Specifically, during operation, the drive signal output by the control component 150 is transmitted to the first motor 134 through the first control port 132. The first motor 134 converts the electrical signal into mechanical displacement or torque, thereby driving the first valve core 136, which is mechanically connected to it, to move axially within the valve cavity. The movement of the valve core changes the flow area of ​​the throttling window between the first inlet and the first outlet, thereby achieving precise control of the hydraulic oil flow rate through the first servo valve 130.

[0032] Specifically, the first motor 134 is a torque motor, including a pair of magnets, a magnetic conductor, a coil, and an elastic support. The coil is electrically connected to a wire introduced from the first control port 132 by welding or crimping. When current flows through the coil, an electromagnetic torque is generated in the magnetic field, driving the coil and its connected components to deflect.

[0033] Specifically, the connection between the first motor 134 and the first valve core 136 can be achieved through a Bourdon tube or a feedback rod.

[0034] like Figure 1 As shown, in some embodiments of the present invention, optionally, the second servo valve 140 further includes a second motor 144 and a second valve core 146, wherein the second motor 144 is electrically connected to the second control port 142; the second valve core 146 is disposed in the second valve chamber 148 of the second servo valve 140 and is located between the second inlet and the second outlet; the second valve core 146 is connected to the second motor 144, and the second motor 144 can drive the second valve core 146 to move under the control of the second control port 142, so as to change the opening degree of the second servo valve 140.

[0035] In this embodiment, for the internal actuator of the second servo valve 140, the present invention provides that the second servo valve 140 includes a second motor 144 and a second valve core 146. The second motor 144 acts as an electro-mechanical converter and is electrically connected to the second control port 142 for receiving electrical signals from the control component 150. Specifically, the control terminal of the second motor 144 is electrically connected to the second control port 142 for receiving weak current signals from the control component 150.

[0036] The second valve core 146 is installed in the second valve chamber 148 of the second servo valve 140. The axial position of the second valve core 146 directly controls the flow area between the second inlet and the second outlet. The second valve core 146 is connected to the second motor 144, so that the second motor 144 generates a corresponding torque or displacement after receiving an electrical signal, thereby driving the second valve core 146 to move. By changing the displacement of the second valve core 146, the opening of the second servo valve 140 can be precisely adjusted, thereby controlling the flow rate of hydraulic oil from the liquid source to the second hydraulic chamber 116. This invention achieves precise linear control of hydraulic flow rate by electrical signals through the design of the second servo valve 140.

[0037] Specifically, during operation, the drive signal output by the control component 150 is transmitted to the second motor 144 through the second control port 142. The second motor 144 converts the electrical signal into mechanical displacement or torque, thereby driving the second valve core 146, which is mechanically connected to it, to move axially within the valve cavity. The movement of the valve core changes the flow area of ​​the throttling window between the second inlet and the second outlet, thereby achieving precise control of the hydraulic oil flow rate through the second servo valve 140.

[0038] Specifically, the second motor 144 is a torque motor, comprising a pair of magnets, a magnetic conductor, a coil, and a resilient support. The coil is electrically connected to a wire introduced from the second control port 142 by welding or crimping. When current flows through the coil, an electromagnetic torque is generated in the magnetic field, driving the coil and its connected components to deflect.

[0039] Specifically, the connection between the second motor 144 and the second valve core 146 can be achieved through a Bourdon tube or a feedback rod.

[0040] In this embodiment, the internal structure of the second servo valve 140 is designed to be equivalent to that of the first servo valve 130, ensuring consistency in structure and function between the two valves. The second servo valve 140 also includes a second motor 144 and a second valve core 146. The second motor 144 is electrically connected to the second control port 142 to receive synchronous control signals. The second valve core 146 controls the passage between the second inlet and the second outlet. Its working principle is exactly the same as that of the first servo valve 130. The second motor 144 drives the second valve core 146 to move according to the electrical signal, thereby adjusting the opening of the second servo valve 140 and controlling the flow rate to the second hydraulic chamber 116. This symmetrical and independent dual-valve structure design of the present invention achieves parallel synchronous drive of the two valves, sharing the hydraulic load.

[0041] Figure 1 As shown, in some embodiments of the present invention, optionally, the first servo valve 130 and the second servo valve 140 are symmetrically distributed with respect to the vibration actuator 110.

[0042] In this embodiment, regarding the spatial layout of the two servo valves, the present invention sets the first servo valve 130 and the second servo valve 140 to be mirror-symmetrically distributed in their installation positions with the central axis of the vibration actuator 110 as the axis of symmetry.

[0043] By symmetrically distributing the first servo valve 130 and the second servo valve 140 relative to the vibration actuator 110, not only is the hydraulic pipeline layout more regular, but more importantly, it ensures that the hydraulic pipelines from the two servo valves to the corresponding hydraulic chambers of the vibration actuator 110 are as consistent as possible in terms of length, bend angle, flow resistance, and other characteristics. This consistency can reduce the phase difference and amplitude difference generated during the transmission of the two hydraulic power sources, which is conducive to a more balanced and synchronized output of the two servo valves, thereby more effectively suppressing vibration waveform distortion in a coordinated manner.

[0044] Specifically, the connection between the first servo valve 130 and the vibration actuator 110, and the connection between the second servo valve 140 and the vibration actuator 110, can be achieved by providing valve block interfaces on both sides of the vibration actuator 110. The first servo valve 130 and the second servo valve 140 are respectively mounted on these two symmetrical valve block interfaces via connectors.

[0045] like Figure 1 As shown, in some embodiments of the present invention, optionally, the vibration actuator 110 includes a hammer 112 and a plate 122, wherein the hammer 112 is provided with a first hydraulic chamber 114 and a second hydraulic chamber 116; the plate 122 is connected to the hammer 112.

[0046] In this embodiment, the vibration actuator 110 mainly consists of a hammer 112 and a plate 122. The hammer 112 has two independent cavities: a first hydraulic cavity 114 and a second hydraulic cavity 116. Hydraulic oil alternately enters these two cavities, driving the hammer 112 and its connected components to reciprocate. The plate 122 is rigidly connected to the lower part of the hammer 112 and is directly coupled to the ground. The impact force generated by the hammer 112 is transmitted to the ground through the plate 122. The design of the vibration actuator 110 in this invention tightly integrates the actuation mechanism and the output mechanism, which is beneficial for efficient force transmission and system miniaturization.

[0047] Specifically, the first hydraulic chamber is the upper chamber, and the second hydraulic chamber is the lower chamber. In this invention, oil is not introduced into the upper and lower chambers simultaneously, but rather in an alternating oil-introducing process. If high-pressure oil is introduced into the upper chamber, low-pressure oil is discharged from the lower chamber, and vice versa. Oil entering the upper chamber pushes the weight upward, while the piston connected to the plate moves downward together, thus exerting a force on the ground. Conversely, oil entering the lower chamber pushes the weight downward, while the piston connected to the plate moves upward together. This alternating oil-in and-out driving mechanism is key to achieving efficient and controllable impact.

[0048] Specifically, the counterweight 112 has a main cavity inside, and a piston 118 is disposed in the main cavity. The piston 118 divides the main cavity to form a first hydraulic cavity 114 located above and a second hydraulic cavity 116 located below. The piston 118 is connected to a piston rod 120, which extends downward and eventually connects to the plate 122.

[0049] Specifically, this invention achieves the reciprocating motion of the hammer 112 and the plate 122 based on the coordinated control of the pressure in the upper and lower chambers. When it is necessary to drive the plate to apply force downwards to the ground, the control component 150 controls the first servo valve 130 to inject high-pressure hydraulic oil into the first hydraulic chamber 114 (upper chamber), while simultaneously controlling the second servo valve 140 to connect the second hydraulic chamber 116 (lower chamber) to the return oil circuit. The oil entering the upper chamber pushes the piston 118 downwards, which in turn drives the plate 122 downwards through the piston rod 120, outputting an impact force to the ground.

[0050] When a system reset is required, the control component 150 changes the command signal output to the dual servo valves. The first servo valve 130 actuates, connecting the first hydraulic chamber 114 (upper chamber) to the return oil circuit, while the second servo valve 140 injects high-pressure oil into the second hydraulic chamber 116 (lower chamber). The oil entering the lower chamber pushes the piston 118 upward, causing the plate 122 to move upward as a whole, completing the reset in preparation for the next impact.

[0051] like Figure 1 As shown, in some embodiments of the present invention, optionally, the seismic source system 100 further includes a detection component, which is used to detect the displacement of the weight 112, the acceleration of the weight 112, the acceleration of the plate 122, the valve core displacement of the first servo valve 130, and the valve core displacement of the second servo valve 140; the control component 150 is electrically connected to the detection component, and the control component 150 is also used to adjust the opening degree of the first servo valve 130 and the second servo valve 140 according to the displacement of the weight 112, the acceleration of the weight 112, the acceleration of the plate 122, the valve core displacement of the first servo valve 130, and the valve core displacement of the second servo valve 140.

[0052] In this embodiment, the seismic source system 100 also includes a detection component, which is used to detect the displacement of the weight 112, the acceleration of the weight 112, the acceleration of the plate 122, the valve core displacement of the first servo valve 130, and the valve core displacement of the second servo valve 140. The detection component provides comprehensive real-time status monitoring for the seismic source system 100. By collecting feedback from multiple parameters such as the displacement and acceleration of the weight 112, the acceleration of the plate 122, and the valve core displacements of the two servo valves, the foundation for closed-loop control is established.

[0053] The control component 150 is electrically connected to the detection component. Based on the real-time data detected by the detection component, the control component 150 can accurately calculate and dynamically adjust the control signals sent to the first servo valve 130 and the second servo valve 140, thereby achieving precise and synchronous adjustment of the valve opening. This closed-loop control strategy of the present invention ensures that the upper and lower chambers operate strictly according to the predetermined alternating oil inlet pattern, that is, when high-pressure oil enters the upper chamber, oil returns smoothly to the lower chamber, and when high-pressure oil enters the lower chamber, oil returns smoothly to the upper chamber, effectively ensuring the synchronicity and accuracy of the reciprocating motion of the counterweight 112 and the plate 122. Ultimately, through this real-time precise control based on multi-parameter feedback, the purity, signal-to-noise ratio, and phase consistency of the system output force waveform are fundamentally enhanced, providing a key guarantee for obtaining high-resolution exploration data.

[0054] like Figure 1 As shown, in some embodiments of the present invention, optionally, the detection component includes a first displacement sensor 170, a first acceleration sensor 172, and a second acceleration sensor 178, wherein the first displacement sensor 170 is disposed on the weight 112 and is used to detect the displacement of the weight 112; the first acceleration sensor 172 is disposed on the weight 112 and is used to detect the acceleration of the weight 112; and the second acceleration sensor 178 is disposed on the plate 122 and is used to detect the acceleration of the plate 122.

[0055] In this embodiment, the control component 150 can acquire the motion trajectory and dynamic characteristics of the hammer 112 in real time through the first displacement sensor 170 and the first acceleration sensor 172 installed on the hammer 112. The second acceleration sensor 178 installed on the plate 122 directly monitors the force signal characteristics transmitted to the ground. These key parameters together constitute the feedback basis of the closed-loop control, enabling the control component 150 to accurately calculate the deviation between the actual motion state of the hammer 112 and the plate 122 and the target waveform, and dynamically adjust the control signals sent to the two servo valves accordingly. This ensures the synchronization accuracy and timing of the alternating entry and exit of hydraulic oil in the upper and lower chambers, and ultimately achieves the output of high-fidelity seismic waveforms.

[0056] Specifically, the first displacement sensor 170 and the first acceleration sensor 172 are both mounted on the weight 112, and are used to detect the actual displacement and acceleration of the weight 112, respectively.

[0057] The first displacement sensor 170 and the first acceleration sensor 172 are electrically connected to the control component 150, and their output signals are fed back to the control component 150. The control component 150 compares the detected displacement and acceleration of the weight with preset parameters of the system. If a deviation exists, the control component 150 adjusts the control signals output to the first and second servo valves 140 in real time, thereby changing the opening degree of the servo valves, correcting the flow and pressure of the hydraulic oil, and ultimately ensuring that the movement of the weight 112 meets the requirements.

[0058] Specifically, the first displacement sensor 170 and the control component 150 are electrically connected via a cable, and the first acceleration sensor 172 and the control component 150 are also electrically connected via a cable. Specifically, when using cable connections, the cable is protected by a flexible metal conduit.

[0059] Specifically, the first displacement sensor 170 and the first acceleration sensor 172 can also be electrically connected to the control component 150 via wireless communication.

[0060] Specifically, during operation, the second accelerometer 178 measures the actual acceleration at the point where the plate 122 couples with the ground. The control component 150 uses this signal to calculate the ground force, which accurately reflects the energy input underground. The controller 152 uses this calculated ground force as the main feedback quantity, compares it with the desired output force signal, and adjusts the servo valve through closed-loop control to ensure that the final excited seismic wave signal has high fidelity.

[0061] Specifically, the second acceleration sensor 178 is mounted on the plate 122 via a threaded connector.

[0062] Specifically, the second acceleration sensor 178 can also be mounted on the plate 122 via a magnetic structure.

[0063] Specifically, the second acceleration sensor 178 is electrically connected to the control assembly 150 via a cable.

[0064] Specifically, the second acceleration sensor 178 can also be electrically connected to the control component 150 via wireless communication.

[0065] like Figure 1 As shown, in some embodiments of the present invention, optionally, the detection component includes a second displacement sensor 180 and a third displacement sensor 182, wherein the second displacement sensor 180 is disposed on the first servo valve 130 and is used to detect the valve core displacement of the first servo valve 130; the third displacement sensor 182 is disposed on the second servo valve 140 and is used to detect the valve core displacement of the second servo valve 140.

[0066] In this embodiment, the detection component further includes a second displacement sensor 180 and a third displacement sensor 182. The second displacement sensor 180 is disposed on the first servo valve 130 and is used to detect the valve core displacement of the first servo valve 130. The third displacement sensor 182 is disposed on the second servo valve 140 and is used to detect the valve core displacement of the second servo valve 140. This invention directly monitors the actual displacement of the valve core by using displacement sensors respectively disposed on two servo valves, providing the control system with the most direct feedback from the front-end actuator.

[0067] Specifically, during operation, the second displacement sensor 180 detects the displacement of the first valve core 136, and the third displacement sensor 182 detects the displacement of the second valve core 146. The control component 150 compares the detected actual valve core displacement with the expected valve core displacement calculated according to the overall control command, monitors the synchronization of the valve core displacements of the two valves, and performs dynamic compensation to ensure balanced output of the two valves.

[0068] Specifically, the second displacement sensor 180 is built into the first servo valve 130, and the third displacement sensor 182 is built into the second servo valve 140.

[0069] Specifically, the second displacement sensor 180 and the third displacement sensor 182 are electrically connected to the control component 150 via cables. Specifically, the displacement signal of the valve core is led out through the multi-core cable of the servo valve and connected to the control component 150.

[0070] Specifically, the second displacement sensor 180 and the third displacement sensor 182 can also be electrically connected to the control component 150 via a wireless connection.

[0071] like Figure 1 As shown, in some embodiments of the present invention, optionally, the control component 150 includes a controller 152 and a junction box 154, wherein the junction box 154 includes a first interface 155, a second interface 156, a third interface 157, a fourth interface 158, a fifth interface 160, a sixth interface 162, and a seventh interface 164. The first interface 155 is electrically connected to the controller 152, the second interface 156 is electrically connected to the first control port 132, the third interface 157 is electrically connected to the second control port 142, the fourth interface 158 is electrically connected to the first displacement sensor 170, the fifth interface 160 is electrically connected to the first acceleration sensor 172, the sixth interface 162 is electrically connected to the second acceleration sensor 178, and the seventh interface 164 is electrically connected to the second displacement sensor 180 and the third displacement sensor 182.

[0072] In this embodiment, the control component 150 is specifically configured to consist of a controller 152 and a junction box 154, with the controller 152 being the main processing element. The junction box 154 serves as a centralized signal relay and distribution hub and is equipped with multiple interfaces.

[0073] The first interface 155 is electrically connected to the controller 152. The first interface 155 and the controller 152 communicate at high speed. Through the first interface 155, the controller 152 can send signals to the junction box 154, and the junction box 154 can also send back signals to the controller 152.

[0074] The second interface 156 is electrically connected to the first control port 132, and the third interface 157 is electrically connected to the second control port 142. The second interface 156 and the third interface 157 respectively output drive current to the control ports of the first and second servo valves 140. The fourth interface 158 is electrically connected to the first displacement sensor 170, the fifth interface 160 is electrically connected to the first acceleration sensor 172, and the sixth interface 162 is electrically connected to the second acceleration sensor 178. The fourth interface 158, the fifth interface 160, and the sixth interface 162 receive feedback signals from the first displacement sensor 170, the first acceleration sensor 172, and the second acceleration sensor 178, respectively. The seventh interface 164 is used to receive valve core displacement sensor signals from the two servo valves. This invention simplifies system wiring, improves the reliability and modularity of electrical connections, facilitates on-site installation, debugging, and maintenance, and enhances the system's anti-interference capability through centralized connection via the junction box 154.

[0075] During operation, the controller 152 can acquire seismic source exploration requirements. Based on these requirements, it generates a first drive signal and a second drive signal, which are two synchronized drive signals. These two drive signals are then sent to the junction box 154. The junction box 154 then distributes the drive signals to two servo valves via a second interface 156 and a third interface 157, thereby adjusting the opening of the first servo valve 130 and the second servo valve 140.

[0076] Junction box 154 serves as the hub for all signal convergence and transfer. Signals from various sensors are sent into junction box 154 through their respective interfaces, and then uploaded to controller 152 through first interface 155. After processing, controller 152 determines whether to adjust, and then sends the generated control command to junction box 154 through first interface 155. Junction box 154 then distributes the drive current to the two servo valves through second and third interfaces 157.

[0077] Specifically, the first interface 155 is connected to the controller 152 via a cable, and can also be connected to the master port of the controller 152 via a cable. The second interface 156 is connected to the first control port 132 of the first servo valve 130 via a cable, and the third interface 157 is connected to the second control port 142 of the second servo valve 140 via a cable. The fourth interface 158, the fifth interface 160, the sixth interface 162, and the seventh interface 164 are connected to the slave sensors via cables. The seventh interface 164 is a multi-pin interface that simultaneously connects to the signal lines of the second and third displacement sensors 182.

[0078] Specifically, Figure 1 Arrow A indicates that the second interface 156 transmits a signal to the first control port 132; arrow B indicates that the third interface 157 transmits a signal to the second control port 142; arrow C indicates that the first displacement sensor 170 transmits a signal to the fourth interface 158; arrow D indicates that the first acceleration sensor 172 transmits a signal to the fifth interface 160; arrow E indicates that the second acceleration sensor 178 transmits a signal to the sixth interface 162; and arrow E also indicates that the second displacement sensor 180 and the third displacement sensor 182 transmit signals to the seventh interface 164.

[0079] In some embodiments of the present invention, the source system in the related art is tested, analyzed, and theoretical verification experiments are conducted.

[0080] Specifically, the seismic source system, or vibration generator used in geological exploration, is the core excitation device in modern geophysical exploration systems, playing an irreplaceable role in fields such as petroleum seismic exploration and deep geological surveys. Its core control unit—the servo valve—serves as the nerve center of the electro-hydraulic conversion system, responsible for accurately converting weak electrical control signals into hydraulic power output. A typical servo valve structure includes a torque motor, a pre-amplifier stage, and a power stage. This actuator, through multi-stage power amplification, can convert milliampere-level drive current into thousands of Newton-meters of hydraulic thrust. Its dynamic response characteristics directly determine the output accuracy and waveform fidelity of the seismic source system.

[0081] For servo valves, the flow-pressure characteristic exhibits a significant nonlinear relationship in both static and dynamic characteristics. According to the fundamental equations of fluid dynamics, the output flow rate of a servo valve is proportional to the square root of the load pressure difference. This nonlinear characteristic, under broadband scanning signal excitation, leads to harmonic distortion in the output force of the hydraulic actuator. Especially in the low-frequency range (<10Hz) and high-frequency range (>80Hz), this nonlinear distortion produces complex modulation effects with the fundamental signal, resulting in second harmonic distortion and phase shift. Ultimately, this leads to a significant increase in the total harmonic distortion (THD) of the controllable source output force waveform, severely degrading the effective bandwidth and dominant frequency energy concentration of the seismic signal.

[0082] The direct impact of this nonlinear distortion is reflected in the signal-to-noise ratio (SNR) of the seismic acquisition data. According to the vibration signal propagation model, the harmonic components of the output force waveform from the controllable source will interfere with the fundamental wave signal during propagation through the strata, forming pseudo-phase axes and false reflection interfaces. Specifically, the expression for the source hydraulic servo flow rate formula is as follows: ; Where Q is the flow rate output by the servo valve's main valve. K is the flow gain coefficient, and X... v It is the displacement of the servo valve's main valve, P. S Supply pressure, P d It is achieved through the pressure difference between the upper and lower chambers of the hammer piston.

[0083] As can be seen from the expression for flow rate above, the flow rate and pressure difference have a square root relationship. This square root is non-linear, which can lead to harmonic distortion. To more accurately analyze the relationship between flow rate and pressure difference in a servo valve, a servo valve flow-pressure curve is introduced. For example... Figure 2 As shown, in the servo valve flow-pressure curve, the horizontal axis represents the normalized load pressure (a percentage calculated based on the maximum load pressure Ps), and the vertical axis represents the normalized servo valve flow rate (a percentage calculated based on the maximum load flow rate QS). This allows for the generation of a series of servo valve flow-pressure curves. Figure 2 As shown, its nonlinear characteristics are mainly manifested in the following three aspects: First, the curve as a whole presents a typical parabolic shape, and this nonlinearity mainly stems from the inherent nonlinear flow characteristics of the valve core throttling orifice; Second, the distortion phenomenon of the flow-pressure characteristic curve is mainly manifested in the spectrum analysis as odd harmonic components dominated by the third and fifth harmonics; Finally, through the curve shape analysis, it can be concluded that when the displacement amplitude of the servo valve increases and the load pressure increases, the nonlinear effect of the system shows a significant strengthening trend.

[0084] By quantitatively analyzing the dynamic characteristics of the servo valve, this invention studies and simulates the working condition of the maximum displacement Xv of the valve core. Figure 3 This demonstrates when the load pressure is greater than P L / P S When the standardized flow rate Q varies continuously within the range of 10%-60%, L / Q S The evolution law is shown in the figure. The blue curve represents the calculation results of the numerical model based on the nonlinear flow-pressure characteristics of the servo valve, while the black dashed line represents the ideal linear characteristic baseline. Further analysis shows that when the PL / PS value is low, the measured curve has a high degree of agreement with the linear baseline; when P... L / P S When the value increases to 60%, the nonlinear distortion rate of the system increases significantly.

[0085] In a controllable vibration source hydraulic actuator, the PL pressure difference essentially corresponds to the actuation pressure difference of the controllable vibration source piston, and its output characteristic can be expressed as F=A×P. L (A is the effective working area of ​​the piston). Since A is a constant, the system output force is linearly positively correlated with PL, which creates a mechanistic contradiction with the nonlinear flow characteristics of the servo valve. To quantitatively characterize this nonlinear coupling effect, a pressure gradient experiment was designed. Measured data shows that when P... L / P S When the nonlinear distortion of the servo valve increases from 10% to 60%, it provides key data support for the design of subsequent nonlinear compensation algorithms.

[0086] Specifically, Figure 4 , Figure 5 and Figure 6 This is performance analysis data of a single-servo valve of a certain type of seismic source system under a 1003Hz constant frequency scan and a 40,000-pound output condition, in related technologies. Figure 4 The "Time Variant Spectral Analysis - 9301-4 SGF" in the text refers to "Time-varying Spectral Analysis - 9301-4 SGF". Figure 5 The term "Harmonic Distortion" refers to "harmonic distortion". Figure 6 The “Absolute Peak Force” in the text refers to the absolute peak force.

[0087] Figure 4 The spectrum is plotted with frequency (Hz) on the vertical axis and time (s) on the horizontal axis. The distribution of signal energy in different frequency bands and its changes over time are displayed intuitively by using color intensity (from blue to red). Warm colors represent high energy, such as the light green area around -26dB, which shows that the signal energy is mainly concentrated at the fundamental frequency.

[0088] Figure 5The harmonic distortion diagram uses three quantization curves to reveal that the total distortion rate is 15%, reflecting the degree of nonlinear distortion of the system. Specifically, the blue line (ODD) represents the distortion rate of odd harmonics, the green line (EVEN) represents the distortion rate of even harmonics, and the red line (THD) represents the total harmonic distortion, which is a comprehensive representation of the distortion of odd and even harmonics.

[0089] Figure 6 The peak force curve further records the process by which the source output force (9301-4 SGF) reaches the set load and remains stable over time. Together, these three factors constitute a complete assessment of the signal quality and harmonic characteristics of this scan.

[0090] Specifically, using the same controlled seismic test with the same scanning parameters, the output power of the controlled seismic source was changed from 40,000 pounds to 60,000 pounds, and the test structure was as follows: Figure 7 , Figure 8 and Figure 9 As shown, where, Figure 7 The "Time Variant Spectral Analysis - 9301-4 SGF" in the text refers to "Time-varying Spectral Analysis - 9301-4 SGF". Figure 8 The term "Harmonic Distortion" refers to "harmonic distortion". Figure 9 The “Absolute Peak Force” in the text refers to the absolute peak force.

[0091] Figure 7 The frequency components change over time using color gradients, with the third harmonic energy significantly increasing to approximately -12 dB (corresponding to the red area in the figure). Figure 8 The quantization curves reveal that the total distortion rate has risen to 24%, with odd harmonics becoming the dominant source of distortion. Figure 9 The dynamic process of the source force being loaded to 60,000 pounds over time and remaining stable is shown.

[0092] The test data of a certain type of seismic source system in the related technology above show that when the servo valve load is relatively small, the nonlinearity of the servo valve flow-pressure curve is not obvious, and the resulting distortion is very small. As the servo valve load increases, the nonlinearity caused by the servo valve becomes more and more obvious, and the resulting distortion becomes higher and higher. Currently, some technologies take advantage of the fact that when the servo valve flow-pressure load is very small, it is close to linear, and the resulting distortion is very small, so the obtained data distortion is exceptionally small. However, this method obtains low harmonic distortion at the cost of some energy loss, and has certain limitations, namely, the servo valve pressure-flow curve is close to linear only when the output is low.

[0093] Actual testing showed that while the single servo valve load remained constant (peak force unchanged), the servo valve displacement changed due to the altered pump flow rate. Using the same controllable vibration source at a 10Hz constant frequency, with 75% output, at the same location, [the following occurred]. Figure 10 As shown, the two colored curves in the test results represent two test data points. In the same location test at a constant frequency of 10Hz and 75% output, the peak forces of the two sets of data represented by the different colored curves are basically the same. The basic force curve in the upper right corner and the absolute peak force curve in the lower right corner both show that the output is in the kilonewton range, indicating that the load conditions are the same. However, due to the change in pump flow, the servo valve displacement (VD) is different. When the VD of one set is stable at 25%, the distortion rate remains stable, while when the VD of the other set continues to increase, the distortion rate rises synchronously.

[0094] Under identical geological conditions and equipment configurations, although the peak output parameters of the two sets of tests were set exactly the same, and the measured total hydraulic system output force amplitudes were nearly identical, the actual effective output force of the seismic source showed significant differences. This contradictory phenomenon stems from the profound influence of the dynamic characteristics of a single servo valve on the output waveform quality.

[0095] In the first set of tests, the displacement (vd) of the single servo valve core remained stable within the middle range of the valve body's linear control interval. Under these conditions, the flow-pressure characteristic curve of the valve core throttling orifice was in an approximately linear segment, and the transient flow rate of the hydraulic oil remained highly synchronized with the command signal. At this time, the time-domain waveform of the force signal output by the system was smooth and regular, and spectrum analysis showed that the fundamental energy accounted for over 92%, with higher-order harmonic components effectively suppressed, proving that the energy conversion efficiency reached its optimal state.

[0096] In contrast, the second set of tests showed a continuously fluctuating and increasing trend in the servo valve core displacement. When vd exceeded the linear operating threshold of the valve body, the pressure-flow gain at the throttle port experienced a nonlinear jump, causing phase lag and amplitude jitter in the hydraulic system. The time-domain waveform exhibited significant clipping distortion and high-frequency glitches, with a surge in the energy of the 3rd and 5th harmonics detected in the spectrum, and the fundamental frequency ratio plummeting to below 78%. Although the peak force sensor reading was similar to the first set, a large amount of energy was dissipated in ineffective harmonic vibrations, resulting in a significant attenuation of the effective fundamental force acting on the formation.

[0097] This experiment verifies the crucial role of the servo valve's dynamic linearity in the output quality of the controllable seismic source. When the valve core's operating point deviates from the linear range, although the system can maintain the apparent peak output, energy redistribution occurs due to nonlinear distortion—the fundamental component is intercepted by higher-order harmonics, leading to a reduction in the effective vibration energy actually transmitted to the formation. Therefore, by optimizing the servo valve control algorithm and constraining the valve core displacement within the linear control range, the fundamental energy conversion rate can be significantly improved, achieving a leap in exploration signal quality under the same hydraulic power consumption. This mechanism provides a key theoretical basis for the design of a dual-servo valve controllable seismic source system.

[0098] like Figure 1 As shown, the vibration source system 100 proposed in this invention inputs high-pressure hydraulic oil into the upper and lower chambers of the counterweight 112 through two synchronous inputs. Compared with a single servo valve vibrator and system that only has one torque motor oil input, in the dual servo valve parallel mode, under the constraint of maintaining a constant total output force, the servo valve displacement is reduced, thereby ensuring that the valve core throttling orifice always works in the near-linear region, which is very beneficial for reducing the distortion caused by the servo valve.

[0099] The core control logic of the 100-electrified source system achieves precise hydraulic power output through a branched drive strategy. The command signals generated by the system control unit are decoupled and converted into two independent, phase-synchronized drive current signals, which act on the electromagnetic coils of the main and slave torque motors, respectively. The main torque motor, acting as the primary control loop, is responsible for tracking the reference phase signal, while the slave torque motor achieves real-time synchronization with the main loop through a dynamic compensation mechanism. The two actuators maintain strict consistency in both the time and frequency domains.

[0100] In the hydraulic power transmission stage, the master and slave servo valve assemblies, driven by synchronous current, respectively regulate the high-pressure oil circuit to precisely inject oil into the upper and lower chambers of the counterweight 112. The alternating pressurization of the upper and lower chambers forms a directionally controllable reciprocating driving force. Compared with the traditional single servo valve architecture, the dual-valve parallel topology significantly optimizes the dynamic characteristics of the valve core through flow distribution. Specifically, under equivalent output force conditions, the parallel structure reduces the flow demand of a single servo valve by about 50%, and the valve core displacement is reduced accordingly. This reduction ensures that the opening of the valve core throttling orifice is always maintained within the linear operating range of the valve body, effectively avoiding the harmonic distortion problem caused by the nonlinear characteristics of the valve orifice under the high flow conditions of traditional single valves.

[0101] From the perspective of system transfer function analysis, the dual-valve parallel structure essentially decomposes the nonlinear element originally concentrated at a single valve port into two parallel weakly nonlinear subsystems. In closed-loop control, this structural characteristic not only reduces the harmonic distortion contribution of a single servo valve but also further suppresses the system-level total harmonic distortion (THD) through cross-coupling compensation in the control algorithm. Experimental data show that this design significantly improves the waveform fidelity of the output force signal, especially in the low-frequency range below 5Hz and the high-frequency range above 80Hz, where phase consistency is significantly improved. This technological breakthrough provides a crucial guarantee for the application of high-precision controllable seismic sources in complex geological exploration.

[0102] To simulate the above theory, data tests were conducted, and the test results are as follows: Figure 11 , Figure 12 , Figure 13 , Figure 14 , Figure 15 and Figure 16 shown, specifically, Figure 11 In this context, "Frequency" refers to frequency. Figure 12 The "Absolute Peak Force" in the text refers to the absolute peak force. Figure 13 In this context, "Phase" refers to the phase, and "deg" is the degree, which are units of phase. Figure 14 The “Signal Plots” in the text refers to signal plots. Figure 15 The term "Harmonic Distortion" refers to harmonic distortion. Figure 16 The “Fundamental Force” in the text refers to the fundamental frequency force.

[0103] During data testing, while maintaining consistency between the fundamental and peak forces, the operating pressure was increased from 3000 psi to 5000 psi. Figure 14 The valve core displacement (VD) shows a significant leftward shift, with the percentage displacement in the 5000psi red area being significantly lower than that in the 3000psi blue area, directly confirming the inverse relationship between pressure and displacement in the servo valve flow formula. Meanwhile, Figure 16 The green curve (5000psi distortion) is significantly lower than the purple curve (3000psi distortion) throughout the entire curve, proving that reducing the valve core displacement effectively suppresses the system's nonlinear distortion. The consistent correlation among the data sets indicates that increasing the working pressure can achieve coordinated control of displacement and distortion, thus verifying the correctness of the theoretical nature of this invention. Furthermore, no abnormal pressure or flow rate mutations were observed in curve 13. Figure 13 The Phase curve in the data converges stably.

[0104] In summary, the tests show that, under the same fundamental force and peak force, increasing the working pressure can effectively reduce the valve core displacement, resulting in reduced distortion. This verifies the theory of reducing servo valve displacement and distortion in this invention. Furthermore, the parallel servo valve design of this invention achieves performance optimization without introducing additional health, safety, or environmental risks.

[0105] like Figure 17 As shown, in some embodiments of the present invention, a control method for a seismic source system is proposed, comprising: S202: Obtain seismic source exploration requirements; S204: Generate the first driving signal and the second driving signal according to the requirements of seismic source exploration; S206: Control the opening degree of the first servo valve according to the first drive signal, and control the opening degree of the second servo valve according to the second drive signal.

[0106] In this embodiment, the control method for the source system proposed in this invention is used for the source system as described in any of the above embodiments, and therefore has all the beneficial effects of any of the above source systems.

[0107] The control method for the seismic source system proposed in this invention first obtains the seismic source exploration requirements, which is the starting point of the control. These requirements are instructions issued based on geological targets. Next, a first driving signal and a second driving signal are generated. This step is the core of the control strategy; the control component calculates the synchronized first and second driving signals required to achieve vibration output. These two signals are essentially current commands to drive the first and second servo valves, respectively. The synchronization and coordination of the dual-valve drive are ensured during signal generation, laying the foundation for the alternating and synchronized entry of hydraulic oil into the upper and lower chambers of the vibration actuator.

[0108] Subsequently, based on the first drive signal, the opening degree of the first servo valve is controlled, and based on the second drive signal, the opening degree of the second servo valve is controlled. This step is the execution process of the control command. The two coordinated electrical signals generated by the control component are applied to the control ports of the first and second servo valves respectively, thereby precisely controlling the displacement of their respective valve cores. Ultimately, this achieves precise and synchronous regulation of the hydraulic oil circuits of the upper and lower chambers of the vibration actuator, ensuring smooth oil return to the lower chamber when high-pressure oil enters the upper chamber, and smooth oil return to the upper chamber when high-pressure oil enters the lower chamber.

[0109] The control method for the seismic source system proposed in this invention ensures that the two servo valves operate synchronously according to a predetermined timing sequence by simultaneously generating and sending two coordinated drive signals. Through the coordinated control of the first and second servo valves, the working pressure difference of a single servo valve is reduced by approximately 50%, effectively avoiding the nonlinear distortion problem under high flow conditions with a single valve, and significantly reducing the total harmonic distortion of the output force waveform. The signal-to-noise ratio and waveform fidelity of the seismic source system output signal are fundamentally improved, especially the phase consistency in the low-frequency and high-frequency bands is greatly enhanced, providing reliable data support for high-resolution oil and gas exploration. Under the same hydraulic power consumption, the effective fundamental wave output force of the seismic source system is higher, energy utilization is improved, and the detection depth is increased. This invention achieves a performance breakthrough through structural innovation, avoiding the safety risks associated with relying solely on ultra-high working pressure, and simultaneously enhancing system reliability and safety.

[0110] Specifically, in actual control, when a 3Hz, 60,000-pound output scan is required, the control component first analyzes the demand and generates two coordinated current command signals conforming to a 3Hz sinusoidal law. These two signals are synchronously sent to the control ports of the first and second servo valves. During operation, when a downward impact force is required, the opening of the first servo valve is controlled to allow high-pressure oil to enter the upper chamber, while the opening of the second servo valve is controlled to allow oil to return from the lower chamber. When the system needs to reset, the second servo valve is controlled to allow high-pressure oil to enter the lower chamber, while the first servo valve is controlled to allow oil to return from the upper chamber. Because the load is borne alternately by the two valves in parallel, the actual working pressure difference of a single servo valve is reduced, thereby directly suppressing the harmonic distortion caused by the high pressure difference and high flow rate of a single valve from a mechanistic perspective, ultimately outputting a pure fundamental force with significantly reduced total harmonic distortion (THD).

[0111] like Figure 18 As shown, in some embodiments of the present invention, optionally, a control method for a seismic source system is proposed, comprising: S302: Obtain seismic source exploration requirements; S304: Generate the first driving signal and the second driving signal according to the requirements of seismic source exploration; S306: Control the opening degree of the first servo valve according to the first drive signal, and control the opening degree of the second servo valve according to the second drive signal; S308: Obtain operating parameters; S310: Obtain the first adjustment signal and the second adjustment signal based on the operating parameters; S312: Control the opening degree of the first servo valve according to the first adjustment signal, and control the opening degree of the second servo valve according to the second adjustment signal.

[0112] In this embodiment, the control method of the seismic source system further includes: acquiring operating parameters; acquiring a first adjustment signal and a second adjustment signal based on the operating parameters; controlling the opening degree of a first servo valve based on the first adjustment signal; and controlling the opening degree of a second servo valve based on the second adjustment signal.

[0113] The process of acquiring operating parameters is the source of information for closed-loop control. The hydraulic system uses various deployed sensors to collect operating parameters in real time that reflect the actual operating status of the seismic source system. These operating parameters serve as the basis for the control system to perform self-calibration.

[0114] Next, the control component acquires adjustment signals and compares the collected actual operating parameters with the expected values ​​corresponding to the exploration requirements, calculating the error. Then, based on a preset control algorithm, it generates a first adjustment signal and a second adjustment signal for correction. Finally, the valve opening is controlled according to the adjustment signals, achieving real-time, dynamic correction of the valve opening.

[0115] In this embodiment, the seismic source system proposed in this invention can not only issue initial commands but also perform real-time feedback and self-optimization based on the actual output response, thereby effectively overcoming control errors caused by internal and external interference. This improves the fidelity and stability of the system's output waveform and its adaptability to complex exploration requirements.

[0116] In some embodiments of the present invention, the operating parameters may optionally include: the valve core displacement of the first servo valve and the valve core displacement of the second servo valve, the displacement of the counterweight, the acceleration of the counterweight, and the acceleration of the plate.

[0117] In this embodiment, the specific content of the operating parameters is defined, including the valve core displacement of the first servo valve and the valve core displacement of the second servo valve, the displacement of the counterweight, the acceleration of the counterweight, and the acceleration of the plate. This invention provides feedback through the combined action of these multiple parameters.

[0118] Specifically, while the seismic source system operates according to the initial command, it monitors the actual movement trajectory of the hammer through the first displacement sensor and the first acceleration sensor, monitors the output signal of the plate through the second acceleration sensor to calculate the actual ground force, and monitors the actual displacement of the valve cores of the two servo valves in real time through the second and third displacement sensors.

[0119] In this embodiment, by monitoring these key operating parameters in real time, the control system can comprehensively grasp the entire working chain state from valve core movement to hammer movement and ground force output. The synchronous monitoring of the dual valve core displacement ensures precise timing control of the alternating entry of hydraulic oil into the upper and lower chambers. The displacement and acceleration parameters of the hammer directly reflect its actual reciprocating motion, and the plate acceleration is a direct representation of the force signal output to the ground. Based on the real-time feedback of these parameters, the control component can dynamically adjust the control signals sent to the dual servo valves, ensuring that the upper and lower chambers work in strict accordance with the "alternating oil intake" mode. That is, when high-pressure oil enters the upper chamber, oil returns synchronously to the lower chamber, and vice versa. This achieves precise control of the amplitude, phase, and harmonic content of the output force waveform, ultimately ensuring high fidelity of the seismic signal output and high quality of the exploration data.

[0120] like Figure 19 As shown, in some embodiments of the present invention, a control device 400 for a seismic source system is proposed, for use in a seismic source system as described in the first aspect. The control device 400 includes a first processing unit 410, a second processing unit 420, and a control unit 430. The first processing unit 410 is used to acquire seismic source exploration requirements; the second processing unit 420 is used to generate a first driving signal and a second driving signal according to the seismic source exploration requirements; the control unit 430 is used to control the opening degree of a first servo valve according to the first driving signal and to control the opening degree of a second servo valve according to the second driving signal.

[0121] In this embodiment, the control device 400 for the source system proposed in this invention is used for the source system as described in any of the above embodiments, and therefore has all the beneficial effects of the source system in any of the above embodiments.

[0122] In this embodiment, the control device 400 of the seismic source system proposed in this invention includes a first processing unit 410, a second processing unit 420, and a control unit 430.

[0123] The first processing unit 410 acquires the seismic source exploration requirements, which is the starting point of control. These requirements are instructions issued based on geological targets. Next, the second processing unit 420 generates a first driving signal and a second driving signal. This step is the core of the control strategy, calculating the synchronized first and second driving signals required to achieve vibration output. These two signals are essentially current commands to drive the first and second servo valves, respectively. Signal generation ensures the synchronicity and coordination of the dual-valve drive, laying the foundation for the alternating and synchronized entry of hydraulic oil into the upper and lower chambers of the vibration actuator.

[0124] Subsequently, the control unit 430 controls the opening degree of the first servo valve according to the first drive signal, and controls the opening degree of the second servo valve according to the second drive signal. This step is the execution process of the control command. Two coordinated electrical signals are applied to the control ports of the first and second servo valves respectively, thereby precisely controlling the displacement of their respective valve cores, and ultimately achieving precise and synchronous regulation of the hydraulic oil circuits of the upper and lower chambers of the vibration actuator, ensuring smooth oil return to the lower chamber when high-pressure oil enters the upper chamber, and smooth oil return to the upper chamber when high-pressure oil enters the lower chamber.

[0125] The control device 400 of the seismic source system proposed in this invention ensures that the two servo valves operate synchronously according to a predetermined timing sequence by simultaneously generating and sending two coordinated drive signals. Through the coordinated control of the first and second servo valves, the working pressure difference of a single servo valve is reduced by approximately 50%, effectively avoiding the nonlinear distortion problem under high flow conditions with a single valve, and significantly reducing the total harmonic distortion of the output force waveform. The signal-to-noise ratio and waveform fidelity of the seismic source system output signal are fundamentally improved, especially the phase consistency in the low-frequency and high-frequency bands is greatly enhanced, providing reliable data support for high-resolution oil and gas exploration. Under the same hydraulic power consumption, the effective fundamental wave output force of the seismic source system is higher, energy utilization is improved, and the detection depth is increased. This invention achieves a performance breakthrough through structural innovation, avoiding the safety risks associated with relying solely on ultra-high working pressure, and simultaneously enhancing system reliability and safety.

[0126] Specifically, in actual control, when a 3Hz, 60,000-pound output scan is required, the control component first analyzes the demand and generates two coordinated current command signals conforming to a 3Hz sinusoidal law. These two signals are synchronously sent to the control ports of the first and second servo valves. During operation, when a downward impact force is required, the opening of the first servo valve is controlled to allow high-pressure oil to enter the upper chamber, while the opening of the second servo valve is controlled to allow oil to return from the lower chamber. When the system needs to reset, the second servo valve is controlled to allow high-pressure oil to enter the lower chamber, while the first servo valve is controlled to allow oil to return from the upper chamber. Because the load is borne alternately by the two valves in parallel, the actual working pressure difference of a single servo valve is reduced, thereby directly suppressing the harmonic distortion caused by the high pressure difference and high flow rate of a single valve from a mechanistic perspective, ultimately outputting a pure fundamental force with significantly reduced total harmonic distortion (THD).

[0127] In some embodiments of the present invention, a storage medium is provided on which a computer program is stored, which, when executed by a processor, implements the steps of the control method for the source system in any of the above embodiments.

[0128] In this embodiment, the storage medium proposed by the present invention implements the steps of the source system control method in any of the above embodiments when the computer program is executed by the processor, and therefore has all the beneficial effects of the source system control method in any of the above embodiments, which will not be repeated here.

[0129] like Figure 20 As shown, in some embodiments of the present invention, an electronic device 500 is proposed. The electronic device 500 includes a storage device 510, a processor 520, and a computer program stored on the storage device 510 and executable on the processor 520. When the processor 520 executes the computer program, it implements the steps of the control method of the source system in any of the above embodiments.

[0130] In this embodiment, the electronic device 500 and processor 520 proposed in this invention implement the steps of the control method of the source system in any of the above embodiments when executing the computer program, and therefore have all the beneficial effects of the control method of the source system in any of the above embodiments, which will not be repeated here.

[0131] The above are preferred embodiments of the present invention. It should be noted that, for those skilled in the art, several improvements and modifications can be made without departing from the principle of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A seismic source system (100), characterized in that, include: Liquid source; Vibration actuator (110), the vibration actuator (110) includes a first hydraulic chamber (114) and a second hydraulic chamber (116). The first servo valve (130) includes a first control port (132), a first liquid inlet and a first liquid outlet. The first liquid inlet is connected to the liquid source and the first liquid outlet is connected to the first hydraulic chamber (114). The second servo valve (140) includes a second control port (142), a second liquid inlet and a second liquid outlet. The second liquid inlet is connected to the liquid source and the second liquid outlet is connected to the second hydraulic chamber (116). A control component (150) is electrically connected to the first control port (132) and the second control port (142), and the control component (150) is used to control the opening degree of the first servo valve (130) and the second servo valve (140).

2. The seismic source system (100) according to claim 1, characterized in that, The first servo valve (130) further includes: The first motor (134) is electrically connected to the first control port (132); The first valve core (136) is disposed in the first valve chamber (138) of the first servo valve (130) and is located between the first liquid inlet and the first liquid outlet. The first valve core (136) is connected to the first motor (134). The first motor (134) can drive the first valve core (136) to move under the control of the first control port (132) to change the opening degree of the first servo valve (130).

3. The seismic source system (100) according to claim 1, characterized in that, The second servo valve (140) also includes: The second motor (144) is electrically connected to the second control port (142); The second valve core (146) is disposed in the second valve chamber (148) of the second servo valve (140) and is located between the second inlet and the second outlet. The second valve core (146) is connected to the second motor (144), and the second motor (144) can drive the second valve core (146) to move under the control of the second control port (142) to change the opening degree of the second servo valve (140).

4. The seismic source system (100) according to claim 1, characterized in that, The first servo valve (130) and the second servo valve (140) are symmetrically distributed relative to the vibration actuator (110).

5. The source system (100) according to any one of claims 1 to 4, characterized in that, The vibration actuator (110) includes: A heavy hammer (112) is provided with a first hydraulic chamber (114) and a second hydraulic chamber (116) inside the heavy hammer (112). The plate (122) is connected to the hammer (112).

6. The seismic source system (100) according to claim 5, characterized in that, The seismic source system (100) also includes: The detection component is used to detect the displacement of the hammer (112), the acceleration of the hammer (112), the acceleration of the plate (122), the valve core displacement of the first servo valve (130), and the valve core displacement of the second servo valve (140). The control component (150) is electrically connected to the detection component. The control component (150) is also used to adjust the opening degree of the first servo valve (130) and the second servo valve (140) according to the displacement of the hammer (112), the acceleration of the hammer (112), the acceleration of the plate (122), the valve core displacement of the first servo valve (130) and the valve core displacement of the second servo valve (140).

7. The seismic source system (100) according to claim 6, characterized in that, The detection component includes: A first displacement sensor (170) is disposed on the weight (112) for detecting the displacement of the weight (112); A first acceleration sensor (172) is disposed on the weight (112) for detecting the acceleration of the weight (112); A second acceleration sensor (178) is disposed on the plate (122) for detecting the acceleration of the plate (122).

8. The control method for the seismic source system according to claim 7, characterized in that, The detection component also includes: A second displacement sensor (180) is disposed on the first servo valve (130) for detecting the valve core displacement of the first servo valve (130); A third displacement sensor (182) is disposed on the second servo valve (140) for detecting the valve core displacement of the second servo valve (140).

9. The seismic source system (100) according to claim 8, characterized in that, The control component (150) includes: Controller (152); The junction box (154) includes a first interface (155), a second interface (156), a third interface (157), a fourth interface (158), a fifth interface (160), a sixth interface (162), and a seventh interface (164). The first interface (155) is electrically connected to the controller (152), the second interface (156) is electrically connected to the first control port (132), the third interface (157) is electrically connected to the second control port (142), the fourth interface (158) is electrically connected to the first displacement sensor (170), the fifth interface (160) is electrically connected to the first acceleration sensor (172), the sixth interface (162) is electrically connected to the second acceleration sensor (178), and the seventh interface (164) is electrically connected to the second displacement sensor (180) and the third displacement sensor (182).

10. A control method for a seismic source system, characterized in that, For a source system as described in any one of claims 1 to 9, characterized in that the control method of the source system comprises: Obtain the seismic source exploration requirements; Based on the required seismic source exploration, a first driving signal and a second driving signal are generated. The opening degree of the first servo valve is controlled according to the first drive signal, and the opening degree of the second servo valve is controlled according to the second drive signal.

11. The control method for the seismic source system according to claim 10, characterized in that, The control method for the seismic source system also includes: Obtain runtime parameters; Based on the operating parameters, obtain the first adjustment signal and the second adjustment signal; The opening degree of the first servo valve is controlled according to the first adjustment signal, and the opening degree of the second servo valve is controlled according to the second adjustment signal.

12. The control method for the seismic source system according to claim 11, characterized in that, The operating parameters include: the valve core displacement of the first servo valve and the valve core displacement of the second servo valve, the displacement of the counterweight, the acceleration of the counterweight, and the acceleration of the plate.

13. A control device for a seismic source system, characterized in that, For a source system as described in any one of claims 1 to 9, the control device for the source system comprises: The first processing unit is used to obtain the seismic source exploration requirements; The second processing unit is used to generate a first driving signal and a second driving signal according to the seismic source exploration requirements. The control unit is configured to control the opening degree of the first servo valve according to the first drive signal, and to control the opening degree of the second servo valve according to the second drive signal.

14. A storage medium having a computer program stored thereon, characterized in that, When the computer program is executed by the processor, it implements the steps of the control method for the source system as described in any one of claims 10 to 12.

15. An electronic device comprising a memory, a processor, and a computer program stored in the memory and executable on the processor, characterized in that, When the processor executes the computer program, it implements the steps of the control method for the source system as described in any one of claims 10 to 12.

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