Long-distance high-speed transmission system

Abstract

The utility model discloses a long-distance high-speed transmission system, which relates to the technical field of hydraulic transmission, and comprises a main supply pump source, a discrete impact pump source, a transmission pipeline and a steady flow valve, the main supply pump source enables transmitted oil to flow from the starting section of the transmission pipeline to the outlet section of the transmission pipeline through pressure difference; the discrete impact pump source comprises a boosting device and a shock wave emitter; the boosted oil is stored in a high-pressure energy accumulator or conveyed into a shock wave emitter, pulse impact is conducted on the oil in the conveying pipeline through the shock wave emitter, a shock wave string formed by the pulse impact disperses and segments the oil into pulse flow sections, and a shock wave front face forces the oil at the front end to roll to the outlet section of the conveying pipeline at a high speed; pulsating impact oil at the outlet section of the transmission pipeline enters a buffer flow channel and an oil outlet flow channel in the steady flow valve through an oil inlet flow channel in the steady flow valve, and shock waves entering the buffer flow channel are buffered and stabilized by the shock wave buffer and then flow out of the oil outlet flow channel of the steady flow valve.

Description

A long-distance high-speed transmission system Technical Field

[0001] This application belongs to the field of hydraulic transmission technology, specifically relating to a long-distance high-speed transmission system. Background Technology

[0002] Large existing factories, such as automobile plants, chemical plants, or steel plants, typically have multiple workshops to meet production needs. Each workshop is equipped with various processing machines, such as lathes, drilling machines, and milling machines. These machines usually require multiple pump stations for operation, resulting in redundant construction of multiple pump stations even for a small work area. The hydraulic system of each pump station is inherently inefficient; the overall efficiency of a motor-driven fixed displacement pump's valve control system is typically around 30%, with the asynchronous motor's efficiency at 80%–87%, the fixed displacement pump's volumetric efficiency at 90%–95%, and the maximum efficiency of the valve-controlled cylinder system at 38%. Without considering overflow losses from the relief valve, this translates to 87% × 95% × 38% = 31.8%. This leads to significant energy waste at multiple pump stations, including those using EHA electro-hydraulic actuators with shortened hydraulic lines. Therefore, a new centralized oil supply system with high-flow-rate pumps and no overflow losses is needed. However, in actual production, due to the distance between each workshop (some are quite far apart), and the different time periods for hydraulic supply demand in each workshop, long-distance transmission of hydraulic oil is necessary to ensure sufficient supply to each workshop. Because the pressure loss along the oil's path is significant during long-distance transmission, increasing the pipe diameter to reduce this pressure loss in typical differential pressure flow increases installation costs. Furthermore, even with medium-diameter transmission pipelines, the flow saturation phenomenon in differential pressure flow is difficult to overcome, leading to insufficient supply and inability to fully meet the demand of each workshop. Specifically, for hydraulic equipment located far away, increased friction loss along long-distance pipelines results in insufficient flow at the end, slowing down equipment response. Therefore, emerging workshop factories require an innovative development of long-distance, discrete, high-speed hydraulic transmission.

[0003] Moreover, for large-scale engineering equipment, such as cement pump trucks that are currently over 70 meters long, the hydraulic pipeline transmission response time is greater than 1 second. If a response time of less than 0.1 seconds is required, conventional diameter pipelines of over 70 meters would require higher pressure from the supply side to achieve supply due to pressure loss along the pipeline. However, due to flow saturation issues, it is difficult to achieve the requirement of a response time of less than 0.1 seconds. Therefore, there is an urgent need to provide a long-distance high-speed transmission system and method to solve the technical problem of long-distance, high-speed, and high-flow-rate pipeline transmission. Summary of the Invention

[0004] This application provides a long-distance high-speed transmission system to solve the technical problem of long-distance, high-speed, and high-flow-rate pipeline transmission in the above-mentioned technical issues, so as to meet the problem that the response time in long-distance pipeline transmission of large engineering machinery such as cement pump trucks with a length of more than 70 meters cannot reach within 0.1s.

[0005] The technical solution adopted in this application is as follows:

[0006] A long-distance high-speed transmission system includes a main supply pump source, a discrete impact pump source, a transmission pipeline, and a flow-stabilizing valve;

[0007] The main supply pump source is connected to the starting section of the transmission pipeline through the delivery pipeline and the first control valve, so that the transmission oil from the main supply pump source flows from the starting section of the transmission pipeline to the outlet section of the transmission pipeline through the pressure difference.

[0008] The discrete impact pump source includes a booster device, a high-pressure accumulator, a shock wave emitter, and a shock wave emitter controller. The shock wave emitter controller controls the rotation or oscillation of the shock wave valve core in the shock wave emitter through a control harness connected to the shock wave emitter. The booster device pressurizes part of the oil in the oil tank or delivery pipeline to a set value, and the pressurized oil is stored in the high-pressure accumulator or delivered to the shock wave emitter. The shock wave emitter is connected to the transmission pipeline, and the shock wave emitter pulses the oil flowing through the transmission pipeline at a set frequency according to the pressure difference. The shock wave series formed by the pulsed impact discretizes the oil flowing from the initial section to the outlet section of the transmission pipeline into segments of pulsed flow. Each segment of pulsed flow is pushed by the subsequent shock wave, so that the oil at the front of the shock wave front is transported at high speed to the outlet section of the transmission pipeline.

[0009] The flow-stabilizing rotary valve includes a valve body and a valve core housed within the valve body. The valve core includes a hemispherical impeller cup that recovers shock waves. The valve body also has an inlet flow channel, an outlet flow channel, and a buffer flow channel connected to the valve core. The inlet flow channel is connected to the outlet section of the transmission pipeline, and a shock wave damper is connected inside the buffer flow channel. The pulsating impact oil from the outlet section of the transmission pipeline enters the buffer flow channel and outlet flow channel of the flow-stabilizing rotary valve through the inlet flow channel. After passing through the inlet flow channel, the pulsating impact oil begins to impact the rotation of the hemispherical impeller cup and is thrown into the outlet flow channel by the impact rotation and centrifugal force of the cup. The shock wave entering the buffer flow channel is buffered and stabilized by the shock wave damper and then flows out from the outlet flow channel of the flow-stabilizing rotary valve.

[0010] The main supply pump source includes a return oil pipe, a main accumulator pump, an auxiliary accumulator, and an output pipeline;

[0011] The main accumulator pump includes a main piston, a counterweight, and a drive mechanism. The drive mechanism is connected to the main piston via a clutch, and the counterweight is positioned above the main piston. A first working chamber is formed below the main piston within the main accumulator pump, and an oil tank is formed above the main piston. The first working chamber is connected to the starting section of a transmission pipeline via a lifting pipeline and a first control valve. When the clutch is engaged, the drive mechanism drives the main piston and counterweight upwards, lifting them to draw oil from the oil tank above the main piston and replenish the first working chamber, thus achieving an oil pumping state. When the clutch is disengaged, the drive mechanism disengages from the main piston and counterweight, and the main piston and counterweight pressurize the oil in the first working chamber by gravity, connecting the oil to the starting section of the transmission pipeline via the lifting pipeline and the first control valve, thus achieving an external oil supply state.

[0012] The auxiliary accumulator adopts a pneumatic accumulator and / or a piston-weight accumulator; the stable output pressure of the first working chamber of the main accumulator pump is set to P1, and the pressure of the second working chamber of the auxiliary accumulator is set to P2, then 95% P1≤P2≤P1.

[0013] The maximum capacity of the second working chamber of the auxiliary accumulator is V2, the maximum flow rate supplied to the hydraulic equipment is Q, and the time required for the main accumulator pump to enter the oil pumping state is t. Then, V2≥Q×t.

[0014] The shock wave emitter includes a shock wave generator, a shock wave valve core, a linear motor, and a shock wave generator cover plate. The shock wave generator is connected to the shock wave generator cover plate, and the shock wave valve core and the linear motor are connected inside the shock wave generator. The linear motor includes a drive ring formed by the stator of a rotary motor annularly disposed inside the shock wave generator, and an annular magnetic strip formed by the rotor of a rotary motor disposed outside the shock wave valve core.

[0015] The shock wave generator also has a high-pressure gas chamber and a detonation chamber that are connected to each other; the detonation chamber has a diaphragm that divides the detonation chamber into a gas chamber and a liquid chamber; the gas chamber is connected to the high-pressure gas chamber, and the detonation chamber corresponds to the small Laval nozzle in the shock wave valve core; the annular magnetic strip can drive the shock wave valve core to rotate or swing under the drive of the drive ring, so as to release or disperse the oil in the detonation chamber into pulse shock waves.

[0016] The high-pressure gas chamber has a first fluid channel for receiving external charging and discharging gas, and also has a throat for a first Laval nozzle that converges and then expands, leading to the gas chamber; the blast chamber has a second fluid channel for receiving external high-pressure fluid and a conical nozzle facing the shock valve core; the shock valve core has multiple small Laval nozzles that correspond to the conical nozzles; the shock generator cover plate has a shock channel connecting the small Laval nozzles and the transmission pipeline;

[0017] By rotating or swinging the small Laval nozzle on the shock valve core, the high-pressure fluid in the small Laval nozzle is suddenly depressurized, causing the gas in the high-pressure chamber to expand and eject a gas flow shock wave from the throat. The gas flow shock wave pushes the high-pressure fluid in the liquid chamber in the explosion chamber through the diaphragm and ejects a liquid flow shock wave through the small Laval nozzle and shock wave channel. Each liquid flow shock wave impacts and drives the hydraulic oil in the transmission pipeline to accelerate forward.

[0018] The valve core includes a rotating shaft, a rotary disk, and multiple hemispherical impeller cups; the rotating shaft is connected to the valve body through bearings, the rotary disk is fixed on the rotating shaft, and multiple hemispherical impeller cups are connected at equal intervals to the outer periphery of the rotary disk;

[0019] Oil containing shock waves impacts the hemispherical impeller cup through the inlet channel, causing the cup to drive the valve core to rotate around the rotating shaft. The shock waves rapidly expand and overflow within the hemispherical impeller cup. The overflowing oil is absorbed by the buffer channel in the centrifugal direction of the hemispherical impeller cup's rotation. The remaining oil is thrown into the outlet channel by the impact, rotation, and centrifugal force of the hemispherical impeller cup. After absorbing the shock waves through the buffer channel, the oil flows to the outlet channel for output.

[0020] A filter is connected in the lifting pipeline, and the hydraulic oil pressure output in the lifting pipeline is greater than the initial pressure in the starting section of the transmission pipeline, and the initial pressure in the starting section of the transmission pipeline is greater than the initial pressure in the outlet section of the transmission pipeline.

[0021] When the booster device pressurizes part of the oil in the tank to the set value, it uses a high-pressure oil pump; when the booster device pressurizes part of the oil in the delivery pipeline to the set value, it uses a high-pressure oil pump or a booster cylinder.

[0022] Due to the adoption of the above technical solution, the beneficial effects achieved by this application are as follows:

[0023] 1. This application relates to a long-distance high-speed transmission system, including a main supply pump source, a discrete impact pump source, a transmission pipeline, and a flow-stabilizing valve; the main supply pump source is connected to the starting section of the transmission pipeline through a delivery pipeline and a first control valve, so as to allow the transmission oil from the main supply pump source to flow from the starting section of the transmission pipeline to the outlet section of the transmission pipeline through a pressure difference; the main supply pump source provided in this application can realize the continuous supply of high-pressure, stable, high-flow-rate pressure oil output.

[0024] 2. The discrete impact pump source includes a high-pressure accumulator, a shock wave emitter, and a shock wave emitter controller. The main supply pump source pressurizes a portion of the oil in the tank or delivery pipeline to a set value. The pressurized oil is stored in the high-pressure accumulator or delivered to the shock wave emitter. The shock wave emitter is connected to the transmission pipeline. Through the shock wave emitter, the oil flowing through the transmission pipeline under pressure difference is subjected to pulsating impact at a set frequency. The shock wave series formed by the pulsating impact discretely segments the oil flowing from the initial section to the outlet section of the transmission pipeline into segments of pulsating flow. Each segment of pulsating flow is pushed by a subsequent shock wave, causing the oil at the front of the shock wave front to be transported at high speed to the outlet section of the transmission pipeline. This application sets a discrete... The discrete impact pump source utilizes the incompressibility of high-pressure oil to create rapid pressure transmission, thereby igniting the expansion and flow of compressed gas. It also utilizes the compressibility of the gas and the spatial volume structure to create the geometric conditions for an airflow shock wave, and the inherent power source of the airflow within the first Laval tube, thus obtaining the first shock wave power source—the airflow shock wave. Furthermore, by utilizing the relatively rigid pushing of the oil by the diaphragm and the relative compressibility of the liquid flow, and leveraging the geometric structure of the second Laval tube, a high-density jet of liquid flow shock wave is formed. This allows the oil at the front of the shock wave to roll at high speed to the outlet section of the transmission pipeline, increasing the flow velocity and volume of the transmitted oil over long distances.

[0025] The bending radius of a typical transmission pipeline is no less than 2.5 times the pipe diameter. For a Φ10 pipeline, there is usually one pipe clamp per meter. The normal differential pressure Δp varies depending on the pipeline length, number of bends and shape, and pipe diameter. It can at least ensure that the transmission oil is delivered to the outlet section of the transmission pipeline according to the normal differential pressure flow.

[0026] In differential pressure flow, a base pressure of not less than 10 MPa can ensure the relative stability of the stiffness of the oil in the transmission pipeline 46, enabling discrete flow transmission in a hydraulic quasi-rigid pipeline (Huang Aiwu, Wang Chengqi, Wang Hongtao. Discrete Flow Transmission and Control in a Hydraulic Quasi-rigid Pipeline [J] Proceedings of the 25th International Conference on Fluid Power and Electromechanical Engineering ICFPMCE). (2024) In order to ensure the pressure stability during the conventional differential pressure flow from the starting section of the transmission pipeline 46 to the outlet section of the transmission pipeline 46, a small differential pressure is selected, thereby keeping the transmission pipeline 46 in a low-velocity laminar flow state. The characteristic dimension d (pipe diameter) of the transmission pipeline 46 and the dynamic viscosity μ of the oil form a viscosor rotation ω=2μ / d regarding the differential pressure flow with a velocity v in the pipeline due to the viscosity of the oil through the pipe wall. Due to the rotational effect of the viscosor rotation ω, rotational momentum is inevitably generated, while the main motion is still the linear motion along the pipeline axis. Therefore, these rotational momentum must cancel each other out. Therefore, an even number is introduced to maintain symmetry and cancellation effect, and the pressure difference between the two ends of the transmission pipeline during low-velocity laminar flow can be obtained:

[0027]

[0028] From the above formula, it can be concluded that the pressure difference head ΔP in the one-dimensional low-speed flow direction is mainly used to provide the tangential motion ω to overcome the symmetry and the viscosity of the oil in 4 sets (8 directions) of the pipe wall and to maintain the flow velocity v in the flow direction.

[0029] This also demonstrates the existence of the swirling motion of the liquid flow under the action of viscous force in the differential pressure flow, which provides conditions for further utilizing shock wave propulsion and reducing pipe wall friction.

[0030] During the propagation of the shock wave at the speed of sound, the velocity of the liquid flow molecular clusters reaches its maximum. That is, the liquid flow molecular clusters cannot exceed their maximum velocity—the speed of sound within the liquid flow (the forward velocity of the density propagation collision, related to hydraulic stiffness, let K). e20 =1.57GPa, the density of No. 46 hydraulic oil is ρ = 850 kg / m³, and the speed of sound in the oil is c = √K e20 / ρ=√1.57*1000000000 / 850=1359m / s). Such a high collision propagation speed makes it impossible for it to achieve density uniformity attenuation and absorption in a single propagation. Instead, it needs to oscillate multiple times within the pipeline, like a shock wave on a lake surface, requiring the assistance of the shore for oscillation and absorption. Only after a long period of back-and-forth oscillation and attenuation within the long transport pipeline will it disappear. With such a high speed, once received by the receiving end, it is not reflected, and there is no energy loss due to back-and-forth oscillation attenuation.

[0031] Thus, high-speed transmission not only overcomes the friction of the pipe wall under the action of differential laminar flow, but also reduces the energy loss of shock wave oscillation in the pipeline or the damage to pipeline oscillation due to the timely reception at the tail end.

[0032] 3. The steady-flow rotary valve includes a valve body and a valve core housed within the valve body. The valve core includes a hemispherical impeller cup that recovers shock waves. The valve body also has an inlet flow channel, an outlet flow channel, and a buffer flow channel connected to the valve core. The inlet flow channel is connected to the outlet section of the transmission pipeline, and a shock wave damper is connected inside the buffer flow channel. After the pulsating impact oil in the transmission pipeline passes through the inlet flow channel, it begins to impact the rotation of the hemispherical impeller cup. A portion of the shock wave enters the buffer flow channel, where a portion of the pulsating shock wave is recovered into the cup due to the retraction of the hemispherical impeller cup. The remaining shock wave energy is absorbed by the buffer flow channel through the centrifugal force of the rotating cup. The pulsating flow portion is thrown into the outlet flow channel by the impact rotation and centrifugal force of the cup. The shock wave entering the buffer flow channel is buffered and stabilized by the shock wave damper and then flows out from the outlet flow channel of the steady-flow rotary valve. This application incorporates a flow-stabilizing valve located at the tail end of a long-distance, high-speed transmission pipeline. For high-speed transmitted shock waves, the hemispherical impeller rotor cup within the flow-stabilizing valve at the pipeline tail end receives the shock wave like a baseball player catching a baseball. After reception, the shock wave is not reflected, thus eliminating energy loss due to back-and-forth oscillation. This allows high-speed transmission to overcome pipe wall friction under pressure differential laminar flow and reduces energy loss or damage to the pipeline caused by shock wave oscillations due to timely reception at the tail end.

[0033] This application incorporates a flow-stabilizing valve, which further eliminates shock wave pulses, resulting in a more stable hydraulic oil output with consistent flow and pressure, thus serving as a remote hydraulic pump source outlet. Attached Figure Description

[0034] The accompanying drawings, which are included to provide a further understanding of this application and form part of this application, illustrate exemplary embodiments and are used to explain this application, but do not constitute an undue limitation of this application. In the drawings:

[0035] Figure 1 is a schematic diagram of a hydraulic long-distance high-speed transmission system according to one embodiment of this application;

[0036] Figure 2 is a schematic diagram of the main supply pump source of a hydraulic long-distance high-speed transmission system according to one embodiment of this application;

[0037] Figure 3 is an enlarged view of point A in Figure 2;

[0038] Figure 4 is a schematic diagram of the structure of a discrete impact pump source of a hydraulic long-distance high-speed transmission system according to one embodiment of this application;

[0039] Figure 5 is a schematic diagram of the structure of a flow-stabilizing valve in a hydraulic long-distance high-speed transmission system according to one embodiment of this application;

[0040] In the picture,

[0041] 1. Return oil pipe; 2. Main accumulator pump; 21. Main piston; 22. Counterweight; 23. Drive mechanism; 3. Filter screen; 4. First working chamber; 5. Oil tank; 6. Second working chamber; 7. Lifting pipeline; 8. Input pipeline; 9. First control valve; 10. Second control valve; 11. Auxiliary accumulator; 12. Secondary piston; 13. Filter storage tank; 14. Centrifugal pump; 15. Oil storage chamber; 16. Pressure regulating piston; 161. Small piston; 162. Large piston; 17. Sealing tire; 18. Support tire; 19. Cover plate; 20. Filter; 24. Shock generator; 25. Shock generator cover plate; 26. Shock valve core; 27. Throat pipe 28. Drive ring; 29. ​​Annular magnetic strip; 30. High-pressure gas chamber; 31. Explosion chamber; 32. Diaphragm; 33. Gas chamber; 34. Liquid chamber; 35. Small Laval nozzle; 36. First fluid channel; 37. Second fluid channel; 38. First Laval nozzle; 39. Conical nozzle; 40. Second Laval nozzle; 41. Valve body; 42. Valve core; 43. Rotating shaft; 44. Rotary disk; 45. Rotary cup; 46. Transmission pipeline; 47. Output pipeline; 48. Shock wave buffer; 49. Oil inlet channel; 50. Recovery channel; 51. Oil outlet channel; 52. Pressure boosting device; 53. Third control valve; 54. High-pressure accumulator. Detailed Implementation

[0042] To more clearly illustrate the overall concept of this application, a detailed explanation is provided below with reference to the accompanying drawings.

[0043] Many specific details are set forth in the following description in order to provide a full understanding of this application. However, this application may also be implemented in other ways different from those described herein. Therefore, the scope of protection of this application is not limited to the specific embodiments disclosed below.

[0044] Furthermore, it should be understood in the description of this application that the terms "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0045] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a communication connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0046] In this application, unless otherwise expressly specified and limited, the "above" or "below" of the second feature can mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediate medium. In the description of this specification, references to terms such as "implementation," "example," "a particular embodiment," "example," or "specific example," etc., indicate that the specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described can be combined in any suitable manner in one or more embodiments or examples.

[0047] Example 1

[0048] This application relates to a long-distance high-speed transmission system, as shown in Figures 1-5, including a main supply pump source, a discrete impact pump source, a transmission pipeline 46, and a flow-stabilizing valve.

[0049] The main supply pump source is connected to the starting section of the transmission pipeline 46 through the delivery pipeline 7 and the first control valve 9, so that the transmission oil of the main supply pump source flows from the starting section of the transmission pipeline 46 to the outlet section of the transmission pipeline 46 through the pressure difference.

[0050] The discrete shock pump source includes a booster device, a high-voltage accumulator, a shock wave emitter, and a shock wave emitter controller. The shock wave emitter controller controls the rotation or oscillation of the shock wave valve core 26 in the shock wave emitter through the control harness connected to the shock wave emitter. The booster device 52 boosts part of the oil in the oil tank 5 or the delivery pipeline 7 to a set value, which can be directly derived from Figure 1 in the attached drawings of the manual. The third control valve 53 is located between the booster device 52 and the high-voltage accumulator 54. The boosted oil is stored in the high-voltage accumulator 54 or transported to the shock wave emitter.

[0051] The shock wave emitter is connected to the transmission pipeline 46. The shock wave emitter pulses the oil flowing through the pressure difference in the transmission pipeline 46 at a set frequency. The shock wave generated by the pulsed impact disperses the oil flowing from the initial section to the outlet section of the transmission pipeline 46 into segments of pulsed flow. Each segment of pulsed flow is pushed by the subsequent shock wave, so that the oil at the front of the shock wave front is transported at high speed to the outlet section of the transmission pipeline 46.

[0052] The flow control valve includes a valve body 41 and a valve core 42 disposed within the valve body 41. The valve core 42 includes a hemispherical impeller cup 45 that recovers shock waves. The valve body 41 also has an inlet channel 49, an outlet channel 51, and a buffer channel that are connected to the valve core 42. The inlet channel 49 is connected to the outlet section of the transmission pipeline 46, and a shock wave damper is connected in the buffer channel. The pulsating impact oil from the outlet section of the transmission pipeline 46 enters the buffer channel and outlet channel of the flow control valve through the inlet channel 49. After passing through the inlet channel, the pulsating impact oil begins to impact the rotation of the hemispherical impeller cup and is thrown into the outlet channel by the impact rotation and centrifugal force of the cup. The shock wave entering the buffer channel is buffered and stabilized by the shock wave damper and then flows out from the outlet channel of the flow control valve.

[0053] The main supply pump source configured in this application enables a continuous, high-pressure, and stable high-flow output. The discrete impact pump source utilizes the incompressibility of the high-pressure oil to rapidly transmit pressure, igniting the expansion and flow of compressed gas. The compressibility of the gas and its spatial volume structure create the geometric conditions for an airflow shock wave, along with the inherent power source of the airflow within the first Laval tube, thus generating the first shock wave power source—an airflow shock wave. Furthermore, the relatively rigid pushing of the oil by the diaphragm 32, combined with the relative compressibility of the liquid flow and the geometric structure of the second Laval tube, forms a high-density jet of liquid flow shock wave. This causes the oil at the shock wave front to roll at high speed to the outlet section of the transmission pipeline 46, increasing the flow velocity for long-distance transmission. The use of a flow-stabilizing valve further eliminates shock wave pulses, resulting in a more stable output pressure. The synergistic effect of the main supply pump source, the discrete impact pump source, and the flow-stabilizing valve enables long-distance, high-speed, and stable flow output from the small-diameter transmission pipeline 46.

[0054] In a preferred embodiment, the main supply pump source includes a return oil pipe 1, a main accumulator pump 2, an auxiliary accumulator 11, and an output pipe 47. The main accumulator pump 2 includes a main piston 21, a counterweight 22, and a drive mechanism 23. The drive mechanism 23 is connected to the main piston 21 via a clutch, and the counterweight 22 is positioned above the main piston 21. A first working chamber 4 is formed below the main piston 21 within the main accumulator pump 2, and an oil tank 5 is formed above the main piston 21 within the main accumulator pump 2. The first working chamber 4 is connected to the transmission pipe 46 via a delivery pipe 7 and a first control valve 9. The segments are connected; when the clutch is engaged, the drive mechanism 23 drives the main piston 21 and the counterweight 22 to move upward, thereby lifting the main piston 21 and the counterweight 22 to draw oil from the oil tank 5 above the main piston 21 and replenish it to the first working chamber 4, thus achieving the oil pumping state; when the clutch is disengaged, the drive mechanism 23 disengages from the main piston 21 and the counterweight 22, and the main piston 21 and the counterweight 22 pressurize the oil in the first working chamber 4 by gravity, connecting the oil to the starting segment of the transmission pipeline 46 through the lifting pipeline 7 and the first control valve 9, thus achieving the external oil supply state.

[0055] The auxiliary accumulator 11 is provided with a second working chamber 6. The first working chamber 4 of the main accumulator pump 2 is connected to the second working chamber 6 of the auxiliary accumulator 11 through the second control valve 10 to complete the purpose of supplying oil to the auxiliary accumulator 11 for energy storage. The second working chamber 6 can assist the first working chamber 4 in jointly transporting oil to the outside through the output pipeline 47. It can also independently transport high-pressure oil to the outside through the output pipeline 47 when the main accumulator pump 2 is in the oil pumping state, so as to ensure that when the main accumulator pump 2 is pumping oil, it can assist in completing the connection between the main supply pump source and the lifting pipeline 7 and the first control valve 9 and the starting section of the transmission pipeline 46 to ensure continuous and stable pressure oil supply.

[0056] When the main supply pump delivers the transmission oil to the starting section of the transmission pipeline 46 via the first control valve through the lifting pipeline 7, the main accumulator pump 2 moves downward under its own weight, causing the hydraulic oil in the first working chamber 4 to be forced into the lifting pipeline 7. The oil then flows out of the transmission pipeline 46 through the lifting pipeline 7 and the first control valve 9. The oil in the lifting pipeline 7 can also partially enter the second working chamber 6 of the auxiliary accumulator 11, putting the auxiliary accumulator 11 in a standby oil storage state and an auxiliary oil supply state. When the main accumulator pump 2 is not in operation, the second working chamber 6 of the auxiliary accumulator 11 feeds back high-pressure oil to the output pipeline 47 until the main accumulator pump 2 re-enters the working state.

[0057] Specifically, the main accumulator pump 2 includes a first cylinder, a main piston 21, a counterweight 22, a pressure regulating piston 16, and a cover plate 19. The main piston 21 is connected inside the first cylinder, and the counterweight 22 is positioned above the main piston 21. An oil storage chamber 15 is opened inside the main piston 21. The pressure regulating piston 16 is connected to the bottom opening of the oil storage chamber 15, and the cover plate 19 is connected to the top opening of the oil storage chamber 15. The main piston 21 divides the first cylinder into upper and lower parts: the upper part is the oil tank 5, and the lower part is the first working chamber 4 that outputs stable pressure. The return oil pipe 1 is also connected to the oil tank 5 at the top of the main accumulator pump 2. The oil tank 5 is connected to the first working chamber 4 inside the main accumulator pump 2 through the input pipe 8 and the first control valve 9. The first control valve 9 can control the oil in the first working chamber 4 to prevent it from flowing back to the oil tank 5 through the input pipe 8. A centrifugal pump 14 is also installed on the input pipeline 8. The oil outlet of the centrifugal pump 14 is connected to the first working chamber 4 of the main accumulator pump 2 through the first control valve 9. The oil suction port of the centrifugal pump 14 is set at the bottom of the oil tank 5 on the upper part of the main accumulator pump 2 through a hose. This allows the oil in the oil tank 5 to be transported to the first working chamber 4 through the centrifugal pump 14, increasing the return oil force from the oil tank 5 into the first working chamber 4.

[0058] A filter storage tank 13 is also provided between the first working chamber 4 and the second control valve 10 of the main accumulator pump 2; a filter screen 3 is connected between the filter storage tank 13 and the first working chamber 4; when the main piston 21 is in the working state, the main piston 21 moves down so that the oil in the first working chamber 4 can enter the filter storage tank 13 through the filter screen 3, and then be output to the auxiliary accumulator 11 or the delivery pipeline 7 through the second control valve 10.

[0059] The auxiliary accumulator 11 includes a secondary piston 12, and a second working chamber 6 is provided below the secondary piston 12 in the auxiliary accumulator 11. The first working chamber 4 is connected to the second working chamber 6 through the second control valve 10 to complete the purpose of supplying oil to the auxiliary accumulator 11 for energy storage. The second working chamber 6 can assist the first working chamber 4 in jointly transporting oil to the outside through the lifting pipeline 7, or transport high-pressure oil to the outside through the lifting pipeline 7 alone when the main accumulator pump 2 is in the oil pumping state, or assist the main accumulator pump 2 in adjusting the pressure or flow of the lifting pipeline 7 when the main accumulator pump 2 is transporting oil to the outside through the lifting pipeline 7, so as to complete the continuous and stable oil supply output of the pump source.

[0060] A sealing structure is connected between the outer periphery of the main piston 21 and the first cylinder. The sealing structure includes a sealing tire 17 and a supporting tire 18. The supporting tire 18 is connected to the main piston 21 and is disposed between the main piston 21 and the first cylinder. By adjusting the pressure in the sealing tire 17 or the supporting tire 18, a movable gap is formed between the main piston 21 and the first cylinder when the main piston 21 moves upward, so that the oil in the oil tank 5 lubricates the main piston 21 through the movable gap, and a sealed contact is formed between the main piston 21 and the first cylinder when the main piston 21 moves downward, so that the main piston 21 pressurizes the oil in the first working chamber 4 of the main accumulator pump 2 under the action of gravity.

[0061] In a preferred embodiment, the auxiliary accumulator 11 adopts a pneumatic accumulator and / or a piston-weight accumulator 22; the stable output pressure of the first working chamber 4 of the main accumulator pump 2 is set to P1, and the pressure of the second working chamber 6 of the auxiliary accumulator 11 is set to P2, then 95% P1≤P2≤P1; the maximum capacity of the second working chamber 6 of the auxiliary accumulator 11 is V2, the maximum flow rate supplied to the hydraulic equipment is Q, and the time required for the main accumulator pump 2 to pump oil is t, then V2≥Q×t.

[0062] In a preferred embodiment, the shock wave emitter includes a shock wave generator 24, a shock wave valve core 26, a linear motor, and a shock wave generator cover plate 25. The shock wave generator 24 is connected to the shock wave generator cover plate 25, and the shock wave valve core and the linear motor are internally connected to the shock wave generator. The shock wave valve core 26 and the linear motor are internally connected to the shock wave generator 24. The linear motor includes a drive ring 28 formed by a rotating motor stator annularly disposed within the shock wave generator 24, and a rotating motor rotor disposed outside the shock wave valve core 26. The annular magnetic strip 29; the shock wave generator 24 also has a high-pressure gas chamber 30 and a burst chamber 31 connected to each other; the burst chamber 31 has a diaphragm 32, which divides the burst chamber 31 into a gas chamber 33 and a liquid chamber 34; the gas chamber 33 is connected to the high-pressure gas chamber 30, and the burst chamber 31 corresponds to the small Laval nozzle 35 in the shock wave valve core 26; the annular magnetic strip 29 can drive the shock wave valve core 26 to rotate or swing under the drive of the drive ring 28, so as to release or disperse the oil in the burst chamber 31 into pulse shock waves.

[0063] The main power supply pump is used to store the oil and energy supplied by the high-pressure oil pump to the explosion chamber 31, and to buffer or replenish the fluctuation of the oil after the shock wave is output from the explosion chamber 31.

[0064] As a preferred embodiment, the high-pressure gas chamber 30 has a first fluid passage 36 for receiving external charging and discharging of gas, and also has a throat 27 of a first Laval nozzle that converges first and then diverges and leads to the gas chamber 33; the blast chamber 31 has a second fluid passage 37 for receiving external high-pressure fluid and a conical nozzle 39 facing the shock valve core 26; the shock valve core 26 has a plurality of small Laval nozzles 35 that can correspond to the conical nozzle 39; the shock generator cover plate 25 has a shock passage connecting the small Laval nozzles 35 and the transmission pipeline 46; by means of the small Laval nozzles 35 on the rotatable or swingable shock valve core, the high-pressure fluid in the small Laval nozzles 35 is suddenly depressurized, thereby causing the gas in the high-pressure gas chamber to expand and a gas shock wave to be ejected from the throat 27. The gas shock wave pushes the high-pressure fluid in the liquid chamber of the blast chamber along the small Laval nozzles 35 through the diaphragm and ejects a liquid shock wave through the shock passage. Each liquid shock wave impacts and drives the hydraulic oil in the transmission pipeline 46 to accelerate and propagate forward.

[0065] When the high-pressure fluid in the conical nozzle 39 is suddenly depressurized, a gas shock wave is ejected from the throat 27. The gas shock wave pushes the high-pressure fluid in the liquid chamber 34 of the blast chamber 31 along the conical nozzle 39 through the diaphragm 32 and ejects it. The high-pressure fluid ejected outward from the conical nozzle 39 is discretized into liquid shock waves by the small Laval nozzles 35 on the rotatable or swingable shock valve core 26. Each shock wave passes through the shock passage, impacts, and drives the hydraulic oil in front of the shock wave in the transmission pipeline 46 to accelerate and propagate forward.

[0066] The high-pressure gas chamber 30 is a rotating body, and one end thereof has a cavity with a hemispherical structure having a sphere radius R; the gas charging and discharging port of the high-pressure gas chamber 30 is directly connected to the cavity of the hemispherical structure; the first Laval nozzle includes a first conical surface, a second conical surface in the high-pressure gas chamber 30, a throat 27 (the radius r of the throat 27 << R) connecting the high-pressure gas chamber 30 and the gas chamber 33 of the blast chamber 31, and a first expansion conical surface formed by the tangential connection of the throat 27 and the spherical surface of the hemispherical cavity of the blast chamber 31; the rotary diameter dimension of the high-pressure gas chamber 30 gradually decreases from the cross-section of the cavity of the hemispherical structure through the first conical surface to the second conical surface; the second conical surface is connected to the throat 27, and the volume V of the cavity of the hemispherical structure of the high-pressure gas chamber 30 11 = 2 / 3πR 3 is equal to the volume V of the cavity surrounded by the first conical surface to the second conical surface 12 =(πR 2 - πr 2 )2 / 3R, then the length from the first conical surface to the second conical surface is approximately 2 / 3R; the volume V1 of the entire high-pressure gas chamber is approximately V 11 + V 12 ≈ 2 / 3πR 3 + 2 / 3πR 3 = 4 / 3πR 3That is, the volume of the sphere with radius R. Through the above setup, the amplitude and planned number of pressure adjustments can be easily calculated and controlled in the aforementioned manner, facilitating control without damaging the diaphragm. Furthermore, after the high-pressure chamber is filled with a preset high-pressure gas, the filling and releasing ports are closed, and the liquid chamber of the burst chamber is filled with high-pressure liquid, causing the diaphragm to expand towards the gas chamber. When the hydraulic oil in the liquid chamber is higher than the outlet pressure of the shock wave channel, the shock wave valve core is driven to rotate or swing via the drive mechanism, connecting the injection channel with the conical nozzle 39 and the shock wave channel. The hydraulic oil in the liquid chamber is ejected first, causing a sudden pressure drop at the diaphragm (e.g., from P1'=33MPa to P2'=20MPa; according to P1'V1'=P2'V2, let the volume of the hemispherical gas in the gas chamber be V'=V1 / 2, the high-pressure chamber...). The volume of the gas is V1 = 2V'. When the diaphragm is not compressed, the total volume of the gas is V0 = 3V'. Therefore, V1' is the volume of the gas chamber when the diaphragm is recessed, making the chamber volume 1 / 3V', i.e., V1' = 1 / 3V' + 2V' = 7 / 3V' = 7 / 6V1 = 7 / 9V0 is the initial volume of expansion. For example, when the pressure decreases from P1' = 33MPa to P2' = 20MPa, V2 = P1'V1' / P2' = 33 / 20 × V1' = 33 / 20 × 7 / 6V1 = V1 + 1 / 6V1 + 0.758V1 ≈ V1 + 1 / 6V1 + 3 / 4V1, and 0.758V1 ≈ 3 / 4V1 ≈ 3 / 4 × 4 / 3πR 3 =πR 3 =πR 2 ×R is exactly the volume of the cylinder formed by the hemispherical radius R of the diaphragm area of ​​the air chamber expanding forward. This causes the high-pressure gas in the air chamber and the high-pressure air chamber to expand and do work. Most of the working airflow in the high-pressure air chamber 30 is compressed inside the first and second conical surfaces before rushing towards the throat 27, forming a continuously accelerating compressed airflow. After passing through the throat 27 and the first expansion cone, it is further expanded and accelerated, thus forming an impact airflow shock wave on the diaphragm 32 in the air chamber 33. Since the air chamber 33 is a hemispherical cavity, the surface area to volume ratio of a sphere is the smallest. The diaphragm 32 must be spherically bulging for optimal performance. Therefore, the airflow shock wave is also a spherically bulging shock wave that continuously oscillates between the high-pressure air chamber 30 and the air chamber 33 and impacts the diaphragm 32. This bulging shock wave is represented as: The wave equation for a positive amplitude exponentially decaying oscillation is given, where P1' is the initial pressure of expansion, k is the decay coefficient with time, t is the oscillation duration, and the oscillation circumferential frequency ω = 2πf'. The hydraulic oil in the impact chamber passes through the diaphragm, causing the outflowing hydraulic oil to be compressed and accelerated through the contraction section. The accelerated hydraulic oil then passes through the second Laval nozzle, forming a liquid flow shock wave. Due to the isothermal process, pV = nRT remains constant. Furthermore, due to the incompressibility of the oil, the volume of the gas oscillating between the high-pressure gas chamber and the gas cavity is related to the shock wave pressure. Inversely proportional, with a phase angle difference of π / 2, since the volume V of the liquid shock wave expanding outward through the diaphragm is equal to the volume of the gas shock wave expanding outward, the volume V of the liquid shock wave can also be obtained by integrating the oscillating wave equation with an exponentially increasing positive amplitude of the agitated gas volume over the duration Δt:

[0067] The volume of the fluid shock wave V=

[0068] In the formula, V1 is the initial volume of the gas expansion between the high-pressure chamber and the gas cavity, k is the decay coefficient with time, t is the oscillation duration, and the oscillation circumferential frequency ω = 2πf. Δt is a natural constant, and Δt is the time it takes for the diaphragm to expand from the concavity in the air cavity to its maximum volume.

[0069] The liquid flow shock wave propagates forward along the oil in the output pipeline, while the airflow shock wave in the gas chamber, under the reaction of the liquid chamber diaphragm, is reflected back to the high-pressure gas chamber through the first Laval tube to form an oscillating shock wave. The oscillation frequency f'≈(2 / 3R×2) / c, where c is the speed of sound in the oil. Therefore, during the time when the drive mechanism drives the shock wave valve core to rotate or swing, connecting the injection channel with the conical nozzle 39 and the shock wave channel, due to the high oscillation frequency f, the diaphragm is subjected to multiple oscillating impacts from the airflow shock wave during the process of the diaphragm going from being concave in the gas chamber to fully expanding into a spherical surface. This also causes the diaphragm to impact the outflowing liquid flow shock wave multiple times. This is beneficial to the accumulation of the thickness δ of the liquid flow shock wave skin, increasing the intensity of the shock wave, so that the liquid flow shock wave carries more liquid density and momentum, and drives the flow parameters in front of the shock wave front to change significantly, such as pressure increase and flow velocity increase, which is beneficial to the rapid discrete transmission of liquid flow in a long-distance pipeline with a diameter d.

[0070] The volume of the fluid shock wave V= During the time it takes for the drive mechanism to rotate or swing the shock valve core, connecting the injection channel with the conical nozzle 39 and the shock channel, and during the process Δt in which the diaphragm expands from the gas chamber to a spherical surface, individual liquid flow shock waves continuously accumulate, forming a spherical shock wave with an inverted volume, like a half-spherical onion. This expands within the shock channel, layering together like the outer and inner layers of a half-onion, creating a forward-convex spherical shock wave. The pressure in front is P2 in the pipeline (e.g., P2 = 20 MPa), and the initial pressure in the explosion chamber behind is P1 (e.g., P1 = 33 MPa). Because of the oil overflow in the explosion chamber, the pressure decreases to a level that balances the pressure in the gas chamber and the pipeline. Therefore, P1... ≤P1 e -kΔt=P2≈20MPa, from which we can calculate t=t2-t0=Δt=ln(P2 / P1) / (-k) (where, the initial time t0=0). The pressure in front of the shock wave is P2 in the pipeline, such as P2=20MPa, and the initial pressure in the explosion chamber behind the shock wave is P1, such as P1=33MPa. P1 is also the initial pressure of the gas in the explosion chamber. Because the oil overflowing from the explosion chamber also reduces the pressure to a level where the pressure in the gas chamber balances the pressure in the pipeline, then:

[0071] P1 ≤P1 e -kΔt =P2≈20MPa

[0072] Therefore, we can calculate:

[0073] t=t2-t0=Δt=(1 / (-k))ln(P2 / P1)

[0074] Let the volume of the hemispherical gas in the gas chamber be V' = V1 / 2, the volume of the gas in the high-pressure gas chamber be V1 = 2V', and the total volume of the gas when the diaphragm is not compressed be V0 = 3V'. Then V1' is the volume of the gas chamber when the diaphragm is recessed into the gas chamber, making the gas chamber volume 1 / 3V' = 1 / 6V1, i.e., V1' = 1 / 3V' + 2V' = 7 / 3V' = 7 / 6V1 = 7 / 9V0 is the initial volume of expansion; Example For example, if the pressure is reduced from P1'=33MPa to P2'=20MPa, according to P1'V1'=P2'V2, we get V2=P1'V1' / P2'=33 / 20×V1'=33 / 20×7 / 6V1=V1+1 / 6V1+0.758V1≈V1+1 / 6V1+3 / 4V1, and 0.758V1≈3 / 4V1=3 / 4×4 / 3πR 3 =πR 3 =πR 2 ×R is exactly gas.

[0075] The volume of the cylinder formed by the forward expansion of the diaphragm area of ​​the cavity and the radius R of the hemisphere;

[0076] At the initial time t0=0, according to the conservation of matter, let the volume of the convex hemispherical cup-shaped body compressed by the shock wave be V3, and the density increase be ρ3=(3 / 4V1) / V3×ρ 液 The velocity is the maximum average value of the molecular cluster motion within the liquid flow, which is equal to the speed of sound c. The inertial force F = (3 / 4V1 × ρ) 液 )×c=ρ3×c×((3 / 4V1) / Δt)_, we can get ρ3=ρ 液 / Δt, combined with the aforementioned ρ3, we can obtain: V3=(3 / 4V1) / Δt=(-k)×(3 / 4V1) / (ln(P2 / P1)), where the negative sign indicates that the volume V3 of the convex hemispherical cup-shaped body compressed by the shock wave is compressed; the volume compressibility (V3 / (3 / 4V1)) is related to the pressure ratio and the attenuation coefficient k; since the shock wave itself is a compression wave, under the action of the inertial force F, the positive shock wave formed in the straight flow channel moves forward, and the front of it is also a strong disturbance compression wave. The change in fluid pressure Δp caused by its disturbance is finite. From the perspective of energy conservation, it will not exceed P1-P2, but it is enough to drive a large change in the flow parameters in front of the shock wave front, such as pressure increase and flow velocity increase. Therefore, the shock wave drives the liquid flow in front to accelerate and roll forward along the pipe wall; since the rear of the shock wave is an expansion wave, the liquid flow behind the shock wave also There exists a small pressure disturbance that propagates in the form of a wave. Its propagation speed is equal to the speed of sound c minus the forward velocity v of the shock wave. The resulting change in fluid pressure is very small, that is, the change in fluid pressure Δp approaches 0 (almost equivalent to the pressure difference of differential flow in the local length of the conveying pipeline 46). This causes slight changes in the flow parameters before and after the disturbance, but it is enough to reduce the friction of the pipe wall on the flow direction of the liquid flow behind it. Moreover, the expansion of the oil behind the shock wave or the suction effect after the inertial movement of the shock wave will accelerate the attraction of the liquid flow to the next shock wave. In the liquid flow in front of the shock wave, the fluid oil crushed by the shock wave front has viscous rotational inertia attached to the wall and is swirled into the rear of the shock wave to form a vortex. It is then pushed by the next shock wave and accelerated to roll, thereby reducing the friction of the pipe wall for the subsequent shock wave, allowing the liquid flow to propagate forward at a high speed close to the speed of sound c.

[0077] because , ×abs(cosωt)≤1, therefore, V3≤V1×(k×Δt+C)=4 / 3πR 3 ×(k×Δt+C), where C is The integral coefficient is C=0 because the amount of oil transmitted by each shock wave is also 0 at Δt=0.

[0078] From Δt = (1 / (-k))ln(P2 / P1), we can obtain the shock volume V3 ≤ V1 × (k × Δt) = 4 / 3πR 3 ×(-ln(P2 / P1))that is, V3≤4 / 3πR 3 ×(-ln(P2 / P1)) That is to say, the larger the radius R of the sphere in the high-pressure gas chamber, when P2 / P1=20 / 33, (-ln(P2 / P1))≈0.5, and the volume of the liquid flow shock wave is approximately 2 / 3πR. 3=V1 is the volume of a hemisphere; when the liquid flow shock wave reaches the 46-diameter d of the delivery pipeline from the second expansion surface, the thickness δ of the liquid flow shock wave skin is just formed. At this time, the molecular clusters inside the shock wave have their own sound speed and move uniformly towards the shock wave front. The conical circular cross-section of the opening of the second expansion surface is equal to the cross-sectional area of ​​the delivery pipeline. Then, the pressure difference before and after the molecular clusters inside the shock wave is 0, that is, the pressure before the molecular clusters inside the shock wave skin is equal to the pressure after the shock wave skin and equal to the pressure inside the delivery pipeline, which is 20MPa; then, when P2 / P1=20 / 33, when (-ln(P2 / P1))≈0.5, the shock wave skin density ρ is:

[0079] ρ=(ρ 液 ×3 / 4V1) / V3≥(ρ 液 ×πR 3 ) / (4 / 3πR 3 ×(-ln(P2 / P1)))=3 / 4ρ 液 / (-ln(P2 / P1))≈3 / 2ρ 液

[0080] In the formula, ρ 液 Let ρ be the density of the liquid, ρ be the shock wave density, and R be the radius of the sphere in the high-pressure gas chamber.

[0081] Furthermore, because the molecular clusters within the shock wave membrane move at the highest sound speed of molecules within the oil fluid, the thickness of the shock wave membrane...

[0082] Although the degree δ is small, the compressible density is relatively large, that is, ρ≥3 / 2ρ. 液 ,but:

[0083] (ρ×V3)×c≥(V3×3 / 4ρ 液 / (-ln(P2 / P1))≈3 / 2ρ 液 ×V3×c

[0084] The large momentum and impact force cause the pressure in front of the shock wave to be greater than the liquid flow pressure in the pipeline. Consequently, the shock wave pushes the oil flowing in front of the shock wave in the pipeline to accelerate forward.

[0085] Under the action of inertial force F, the normal shock wave formed in the straight flow channel moves forward. Because the front of the shock wave is a strong disturbance compression wave, the pressure change Δp caused by the disturbance is finite, but sufficient to drive a significant change in the flow parameters ahead of the shock wave front, such as pressure increase and velocity acceleration. Therefore, the shock wave propels the liquid flow ahead to accelerate and roll forward along the pipe wall. Furthermore, because the rear of the shock wave is an expansion wave, a small pressure disturbance also exists in the liquid flow behind the shock wave, propagating in the form of a wave. The pressure change caused by this is very small, that is, the pressure change Δp approaches... The change in flow parameters before and after the disturbance is small, but sufficient to reduce the friction of the pipe wall on the flow path of the subsequent liquid flow. Moreover, the suction effect caused by the expansion of the oil behind the shock wave or the inertial movement of the shock wave will accelerate the suction flow of the liquid flow. In the liquid flow in front of the shock wave, the fluid oil crushed by the shock wave front has viscous rotational inertia attached to the wall and is swirled into the rear of the shock wave to form a vortex. It is then pushed by the next shock wave and accelerated to roll, thereby reducing the friction of the pipe wall for subsequent shock waves, allowing the liquid flow to propagate forward at a speed close to the speed of sound c.

[0086] In a preferred embodiment, the valve core 42 further includes a rotating shaft 43, a rotary disk 44, and a plurality of hemispherical impeller cups 45; the rotating shaft 43 is connected to the valve body 41 by bearings, the rotary disk 44 is fixed on the rotating shaft 43, and the plurality of hemispherical impeller cups 45 are equally spaced on the outer periphery of the rotary disk 44;

[0087] The oil containing shock waves impacts the hemispherical impeller cup 45 through the oil inlet channel 49, causing the cup 45 to drive the valve core 42 to rotate around the rotating shaft 43. The shock waves expand rapidly and overflow within the hemispherical impeller cup 45. The overflowing oil is absorbed by the buffer channel in the centrifugal direction of the rotation of the hemispherical impeller cup 45. The remaining oil is thrown into the oil outlet channel 51 by the impact, rotation, and centrifugal action of the hemispherical impeller cup 45. The oil that has absorbed the shock waves through the buffer channel flows to the oil outlet channel 51 for output.

[0088] Specifically, the steady-flow valve includes a valve body 41, a valve core 42, a shock wave damper 48, and a sensor. The valve body 41 has a support groove, a cavity, an oil inlet channel 49, a recovery channel 50, and an oil outlet channel 51. Bearings are installed in the support groove. The valve core 42 includes a rotating shaft 43, a rotary disk 44, and multiple rotating cups 45 disposed within the cavity. Both ends of the rotating shaft 43 are connected to bearings in the support groove. The rotary disk 44 is fixedly connected to the middle of the rotating shaft 43 with the rotating shaft 43 as its axis. Multiple rotating cups 45 are equally spaced and connected to the outer periphery of the rotary disk 44. The sensor is disposed outside the rotating cavity of the rotating cups 45 within the valve body 41. The centerlines of the oil inlet channel 49 and the oil outlet channel 51 are collinear and tangent to the movement trajectory of the center of the rotating cups 45. The opening of the rotating cup 45 at the tangent point faces the oil inlet channel 49. A recovery channel 50 is opened at the tangent point along the radial direction of the valve core 42, and a shock wave buffer 48 is installed at the bottom of the recovery channel 50. The oil containing the shock wave impacts the rotating cup 45 through the oil inlet channel 49, causing the rotating cup 45 to drive the valve core 42 to rotate around the rotating shaft 43. The shock wave expands rapidly and splashes out inside the rotating cup 45. The splashed oil enters the recovery channel 50 through the centrifugal force of the rotating cup 45, and the shock wave energy of this part of the oil is absorbed by the shock wave buffer 48 at the bottom of the recovery channel 50. Part of the remaining oil in the rotating cup 45 is thrown into the oil outlet channel 51 by the impact, rotation and centrifugal force of the rotating cup 45, and part enters the next impact cycle with the rotation of the rotating cup 45. When the shock wave propagates at the speed of sound, the hemispherical impeller rotating cup of the receiving end stabilizing valve receives the recovered shock wave like a baseball player catching a baseball. It is not reflected after receiving the shock wave, so there is no energy loss due to back-and-forth oscillation in the transmission pipeline 46. This allows high-speed transmission to not only overcome pipe wall friction under pressure differential laminar flow, but also reduce energy loss or damage to pipe oscillations due to timely reception at the tail end.

[0089] In a preferred embodiment, a filter 20 is connected to the lifting pipeline 7, and the hydraulic oil pressure output from the lifting pipeline 7 is greater than the initial pressure in the starting section of the transmission pipeline 46, and the initial pressure in the starting section of the transmission pipeline 46 is greater than the initial pressure in the outlet section of the transmission pipeline 46; when the pressure boosting device boosts part of the oil in the oil tank to the set value, the pressure boosting device uses a high-pressure oil pump; when the pressure boosting device boosts part of the oil in the lifting pipeline to the set value, the pressure boosting device uses a high-pressure oil pump or a booster cylinder.

[0090] The pressure in the delivery pipeline 7 is greater than 7 MPa, preferably 10 MPa.

[0091] For any parts not mentioned in this application, existing technologies may be used or referenced.

[0092] The various embodiments in this specification are described in a progressive manner. The same or similar parts between the various embodiments can be referred to each other. Each embodiment focuses on describing the differences from other embodiments.

[0093] The above description is merely an embodiment of this application and is not intended to limit the scope of this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the scope of the claims of this application.

Claims

1. A long-distance high-speed transmission system, characterized in that, The system includes a main supply pump, a discrete impact pump, a transmission pipeline, and a flow-regulating valve. The main supply pump is connected to the starting section of the transmission pipeline via a delivery pipeline and a first control valve to transfer the transmission oil from the starting section of the transmission pipeline to the outlet section via a pressure difference. The discrete impact pump includes a booster device, a high-pressure accumulator, a shock wave emitter, and a shock wave emitter controller. The shock wave emitter controller controls the rotation or oscillation of the shock wave valve core in the shock wave emitter via a control harness connected to the shock wave emitter. The booster device pressurizes a portion of the oil in the tank or delivery pipeline to a set value, and the pressurized oil is stored in the high-pressure accumulator or transported to the shock wave emitter. The shock wave emitter is connected to the transmission pipeline and pulses the oil flowing through the transmission pipeline via a pressure difference at a set frequency. The shock wave train formed by the pulsed impact propels the starting section of the transmission pipeline. The oil flowing from the initial section to the outlet section is discretely segmented into pulsating flows. Each pulsating flow is pushed by a subsequent shock wave, causing the oil at the front of the shock wave to roll at high speed and be transported to the outlet section of the transmission pipeline. The flow stabilizing valve includes a valve body and a valve core disposed within the valve body. The valve core includes a hemispherical impeller cup that recovers the shock wave. The valve body also has an inlet flow channel, an outlet flow channel, and a buffer flow channel connected to the valve core. The inlet flow channel is connected to the outlet section of the transmission pipeline, and a shock wave damper is connected in the buffer flow channel. The pulsating impact oil in the outlet section of the transmission pipeline enters the buffer flow channel and outlet flow channel of the flow stabilizing valve through the inlet flow channel. After entering the inlet flow channel, the pulsating impact oil begins to impact the rotation of the hemispherical impeller cup and is thrown into the outlet flow channel by the impact rotation and centrifugal force of the cup. The shock wave entering the buffer flow channel is buffered and stabilized by the shock wave damper and then flows out from the outlet flow channel of the flow stabilizing valve.

2. The long-distance high-speed transmission system as described in claim 1, characterized in that, The main supply pump source includes a return oil pipe, a main accumulator pump, an auxiliary accumulator, and an output pipeline; the main accumulator pump includes a main piston, a counterweight, and a drive mechanism; the drive mechanism is connected to the main piston via a clutch, and the counterweight is positioned above the main piston; A first working chamber is formed below the main piston in the main accumulator pump, and an oil tank is formed above the main piston. The first working chamber is connected to the starting section of the transmission pipeline through a lifting pipeline and a first control valve. When the clutch is engaged, the drive mechanism drives the main piston and the counterweight to move upward, thereby lifting the main piston and the counterweight to draw oil from the oil tank above the main piston and replenish the first working chamber, achieving the oil pumping state. When the clutch is disengaged, the drive mechanism is disengaged from the main piston and the counterweight, and the main piston and the counterweight pressurize the oil in the first working chamber by gravity, connecting the oil to the starting section of the transmission pipeline through the lifting pipeline and the first control valve, thereby achieving the external oil supply state.

3. The long-distance high-speed transmission system as described in claim 2, characterized in that, The auxiliary accumulator adopts a pneumatic accumulator and / or a piston-weight accumulator; the stable output pressure of the first working chamber of the main accumulator pump is set to P1, and the pressure of the second working chamber of the auxiliary accumulator is set to P2, then 95% P1≤P2≤P1.

4. The long-distance high-speed transmission system as described in claim 3, characterized in that, The maximum capacity of the second working chamber of the auxiliary accumulator is V2, the maximum flow rate supplied to the hydraulic equipment is Q, and the time required for the main accumulator pump to enter the oil pumping state is t. Then, V2≥Q×t.

5. The long-distance high-speed transmission system as described in claim 1, characterized in that, The shock wave emitter includes a shock wave generator, a shock wave valve core, a linear motor, and a shock wave generator cover plate. The shock wave generator is connected to the shock wave generator cover plate, and the shock wave valve core and the linear motor are connected inside the shock wave generator. The linear motor includes a drive ring formed by the stator of a rotary motor annularly disposed inside the shock wave generator, and an annular magnetic strip formed by the rotor of a rotary motor disposed outside the shock wave valve core.

6. The long-distance high-speed transmission system as described in claim 5, characterized in that, The shock wave generator also has a high-pressure gas chamber and a detonation chamber that are connected to each other; the detonation chamber has a diaphragm that divides the detonation chamber into a gas chamber and a liquid chamber; the gas chamber is connected to the high-pressure gas chamber, and the detonation chamber corresponds to the small Laval nozzle in the shock wave valve core; the annular magnetic strip can drive the shock wave valve core to rotate or swing under the drive of the drive ring, so as to release or disperse the oil in the detonation chamber into pulse shock waves.

7. The long-distance high-speed transmission system as described in claim 6, characterized in that, The high-pressure gas chamber has a first fluid channel for receiving external charging and discharging gas, and a throat with a first Laval nozzle that converges and then expands, leading to the gas chamber; the explosion chamber has a second fluid channel for receiving external high-pressure fluid and a conical nozzle facing the shock valve core; the shock valve core has multiple small Laval nozzles that correspond to the conical nozzles; the shock wave generator cover plate has a shock wave channel connecting the small Laval nozzles and the transmission pipeline; by rotating or swinging the small Laval nozzles on the shock valve core, the high-pressure fluid in the small Laval nozzles is suddenly depressurized, causing the gas in the high-pressure gas chamber to expand and eject a gas flow shock wave from the throat. The gas flow shock wave pushes the high-pressure fluid in the liquid chamber of the explosion chamber through the diaphragm and ejects a liquid flow shock wave along the small Laval nozzles through the shock wave channel. Each liquid flow shock wave impacts and drives the hydraulic oil in the transmission pipeline to accelerate forward.

8. The long-distance high-speed transmission system as described in claim 1, characterized in that, The valve core includes a rotating shaft, a rotary disk, and multiple hemispherical impeller cups. The rotating shaft is connected to the valve body via bearings, the rotary disk is fixed on the rotating shaft, and the multiple hemispherical impeller cups are equally spaced on the outer circumference of the rotary disk. Oil containing shock waves impacts the hemispherical impeller cups through the oil inlet channel, causing the cups to drive the valve core to rotate around the rotating shaft. The shock waves rapidly expand and overflow within the hemispherical impeller cups. The overflowing oil absorbs the shock waves through the buffer channel in the centrifugal direction of the hemispherical impeller cups' rotation. The remaining oil is thrown into the oil outlet channel by the impact, rotation, and centrifugal force of the hemispherical impeller cups. The oil that has absorbed the shock waves through the buffer channel flows to the oil outlet channel for output.

9. A long-distance high-speed transmission system as described in claim 1, characterized in that, A filter is connected in the lifting pipeline, and the hydraulic oil pressure output in the lifting pipeline is greater than the initial pressure in the starting section of the transmission pipeline, and the initial pressure in the starting section of the transmission pipeline is greater than the initial pressure in the outlet section of the transmission pipeline.

10. A long-distance high-speed transmission system as described in claim 9, characterized in that, When the booster device pressurizes part of the oil in the tank to the set value, it uses a high-pressure oil pump; when the booster device pressurizes part of the oil in the delivery pipeline to the set value, it uses a high-pressure oil pump or a booster cylinder.

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