Long-distance high-speed transmission system and method

Abstract

The invention discloses a long-distance high-speed transmission system and method, and relates to the technical field of hydraulic transmission, the long-distance high-speed transmission system 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

Technical Field

[0001] This application belongs to the technical field of hydraulic transmission, and specifically relates to a long-distance high-speed transmission system and method. Background Art

[0002] Existing large factories, such as automobile factories, chemical plants, or steel mills, etc., generally have multiple operating workshops for each factory to meet the needs of production and manufacturing. There are various mechanical equipment for processing and production in each operating workshop, such as lathes, drill presses, milling machines, etc. These mechanical equipment usually require the establishment of multiple pump stations for control, resulting in the problem of repeated construction of multiple pump stations even in a small working area. Because the working efficiency of the hydraulic system of each pump station itself is not high, the overall efficiency of a valve control system of a fixed-displacement pump driven by an electric motor is usually about 30%. Among them, the efficiency of an asynchronous motor is 80% - 87%, the volumetric efficiency of the fixed-displacement pump is 90% - 95%, and the maximum efficiency of the valve control cylinder system is 38%. Without considering the overflow loss of the relief valve, 87%×95%×38% = 31.8%. This leads to a large amount of energy waste in multiple pump stations, including the pump stations of EHA electro-hydraulic actuators with shortened hydraulic pipelines. There is a need for a new centralized oil supply pump source without large overflow losses. However, in actual production, since there is a certain distance between each workshop, some workshops are far apart, and the hydraulic supply demand time periods of each workshop are different. In order to achieve sufficient supply of hydraulic oil to each workshop, it is necessary to achieve long-distance transmission of hydraulic oil. Due to the relatively large frictional pressure loss of the oil during long-distance transmission, in order to reduce the frictional pressure loss in general differential pressure flow and increase the diameter of the transmission oil pipeline, the laying cost will increase. Moreover, even if a medium-diameter transmission pipeline is selected, it is difficult to overcome the flow saturation phenomenon existing in differential pressure flow, which leads to insufficient supply and cannot fully meet the usage requirements of each workshop. That is, for the transmission of hydraulic equipment at a relatively long distance, it will cause a new problem that the end flow supply is insufficient due to the increased frictional loss of the long-distance transmission pipeline, resulting in a slow response of the equipment. Therefore, emerging workshop factories need an innovative development of hydraulic long-distance discrete high-speed transmission.

[0003] Moreover, for large engineering equipment, such as the hydraulic pipeline transmission response time in a cement pump truck currently more than 70 meters long is greater than 1 s. If the response time is required to be within 0.1 s, for a 70-meter-long long-distance transmission of a conventional diameter pipeline, due to the problem of frictional pressure loss, the supply end needs to give a higher pressure to achieve supply. However, due to the flow saturation problem, it is difficult to meet the requirement of a response time within 0.1 s. 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 large-flow transmission of pipelines. Summary of the Invention

[0004] The present application provides a long-distance high-speed transmission system and method to solve the technical problem of long-distance high-speed large-flow transmission in pipelines among the above technical problems, so as to meet the rapid supply of high-pressure oil between workshops or the problem that the response time in the long-distance pipeline transmission of large construction machinery such as a cement pump truck over 70 meters cannot reach within 0.1 s.

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

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

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

[0008] The discrete shock pump source includes a boosting device, a high-pressure accumulator, a shock wave emitter, and a shock wave emission controller; the shock wave emission controller controls the rotation or swing of the shock wave spool in the shock wave emitter through a control wire harness connected to the shock wave emitter; the boosting device boosts a part of the oil in the fuel tank or the lifting pipeline to a set value, and the boosted 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 pulsating shocks are applied to the oil flowing in the transmission pipeline through the pressure difference at a set frequency by the shock wave emitter. The shock wave train formed by the pulsating shocks discretely segments the oil flowing from the starting section to the outlet section in the transmission pipeline into segments of pulsating flow, and each segment of pulsating flow is pushed by the subsequent shock wave, so that the oil at the front end of the shock wave front is transported to the outlet section of the transmission pipeline at high speed by rolling.

[0009] The flow-stabilizing rotary valve includes a valve body and a valve core arranged in the valve body. The valve core includes a hemispherical impeller rotary cup for recovering shock waves. The valve body is also provided with an oil inlet flow channel, an oil outlet flow channel, and a buffer flow channel communicating with the valve core; the oil inlet flow channel is communicated with the outlet section of the transmission pipeline, and a shock wave buffer is connected in the buffer flow channel; the pulsating shock oil in the outlet section of the transmission pipeline enters the buffer flow channel and the oil outlet flow channel in the flow-stabilizing rotary valve through the oil inlet flow channel. After the pulsating shock oil enters the oil inlet flow channel, it starts to impact the hemispherical impeller rotary cup to rotate, and is thrown into the oil outlet flow channel by the impact rotation and centrifugal action of the rotary cup; the shock wave entering the buffer flow channel is buffered and stabilized by the shock wave buffer and then also flows out from the oil outlet flow channel of the flow-stabilizing rotary valve.

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

[0011] The main energy storage pump includes a main piston, a weight, and a driving mechanism; the driving mechanism is connected to the main piston through a clutch, and the weight is arranged above the main piston; a first working chamber is opened below the main piston located inside the main energy storage pump, and a fuel tank is formed above the main piston located inside the main energy storage pump. 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 driving mechanism is used to drive the main piston and the weight to move upward, realizing the lifting of the main piston and the weight, so as to extract and supplement the oil in the fuel tank above the main piston into the first working chamber, realizing the oil pumping state; when the clutch is disengaged, the driving mechanism is separated from the main piston and the weight, and the main piston and the weight rely on gravity to pressurize the oil in the first working chamber, and connect the oil through the lifting pipeline and the first control valve to the starting section of the transmission pipeline, so as to realize the state of supplying oil outward.

[0012] The auxiliary energy storage device adopts a bladder type energy storage device and / or a piston weight type energy storage device; the stable output pressure of the first working chamber of the main energy storage pump is set as P1, and the set pressure of the second working chamber of the auxiliary energy storage device is P2, then 95%P1 ≤ P2 ≤ P1; the maximum capacity of the second working chamber of the auxiliary energy storage device is V2, the maximum flow rate supplied to the hydraulic equipment is Q, and the required time for the main energy storage pump to be in the oil pumping state is t, then V2 ≥ Q×t.

[0013] The shock wave emitter includes a shock wave generating body, a shock wave valve core, a linear motor, and a cover plate; the shock wave generating body is connected to the cover plate, and a shock wave valve core and a linear motor are connected inside the shock wave generating body; the linear motor includes a rotating motor stator annularly arranged to form a driving ring inside the shock wave generating body, and a rotating motor rotor arranged to form an annular magnetic strip outside the shock wave valve core;

[0014] There is also a high-pressure gas chamber and a detonation chamber connected to each other inside the shock wave generating body; there is a diaphragm inside the detonation chamber, and the detonation chamber is separated into a gas chamber and a liquid chamber by the diaphragm; the gas chamber is connected to the high-pressure gas chamber, and the detonation chamber corresponds to a small Laval nozzle inside 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 driving ring, so as to release or disperse the oil in the detonation chamber into pulsed shock waves.

[0015] The high-pressure gas chamber has a first fluid passage for receiving external charging and discharging of gas, and also has the throat of a first Laval nozzle that converges first and then expands leading to the gas chamber; the detonation chamber has a second fluid passage for receiving external high-pressure fluid and a conical nozzle facing the shock wave valve core; the shock wave valve core has a plurality of small Laval nozzles that can correspond to the conical nozzle; the cover plate has a shock wave passage connecting the small Laval nozzles and the transmission pipeline;

[0016] Through the small Laval nozzle on the rotating or swinging shock valve core, the high-pressure fluid in the small Laval nozzle is suddenly depressurized, which causes the gas in the high-pressure gas chamber to expand and the airflow shock wave to be ejected from the throat. The airflow shock wave pushes the high-pressure fluid in the liquid chamber of the detonation chamber through the diaphragm and ejects the liquid flow shock wave along the small Laval nozzle through the shock wave channel. Each liquid flow shock wave impacts and drives the hydraulic oil in the transmission pipeline to accelerate and propagate forward.

[0017] The valve core includes a rotating shaft, a rotating disc and a plurality of hemispherical impeller cups; the rotating shaft is connected to the valve body through a bearing, the rotating disc is fixed on the rotating shaft, and a plurality of hemispherical impeller cups are equally spaced and connected to the outer periphery of the rotating disc;

[0018] The oil liquid containing shock waves impacts the hemispherical impeller cups through the oil inlet flow channel, causing the cups to drive the valve core to rotate around the rotating shaft, and the shock waves rapidly expand and overflow in the hemispherical impeller cups. The overflowing oil liquid is absorbed by the shock wave through the buffer flow channel in the centrifugal direction of the rotation of the hemispherical impeller cups; the remaining oil liquid is thrown into the oil outlet flow channel along with the impact rotation and centrifugal action of the hemispherical impeller cups; the oil liquid flowing out of the buffer flow channel after absorbing the shock wave flows to the oil outlet flow channel for output.

[0019] A filter is connected in the delivery pipeline, and the pressure of the hydraulic oil output in the delivery 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; when the boosting device boosts a part of the oil liquid in the fuel tank to the set value, the boosting device uses a high-pressure oil pump; when the boosting device boosts a part of the oil liquid in the delivery pipeline to the set value, the boosting device uses a high-pressure oil pump or a boosting cylinder.

[0020] This application also relates to a long-distance high-speed transmission method. Based on the above-mentioned long-distance high-speed transmission system, the method specifically includes:

[0021] The main supply pump source delivers the transmission oil liquid to the starting section of the transmission pipeline in a bypass manner through the delivery pipeline via the first control valve;

[0022] The transmission oil liquid is conveyed to the outlet section of the transmission pipeline by conventional pressure difference flow through the transmission pipeline; the basic pressure of the outlet section of the transmission pipeline is not less than 10 MPa;

[0023] The straight section of the starting section of the transmission pipeline is connected to the shock wave emitter. The shock wave emission controller controls the rotation or swing of the shock wave valve core in the shock wave emitter through the control wire harness connected to the shock wave emitter, so that the shock wave emitter emits shock wave liquid flows at a set frequency and pulsates and impacts the oil liquid in the straight section of the starting section of the transmission pipeline. The shock wave liquid flows assist in pushing the oil liquid conveyed by conventional pressure difference flow in the transmission pipeline to overcome the frictional force of the pipe wall on the flow, so that the oil liquid at the front end of the shock wave liquid flow is conveyed at high speed to the outlet section of the transmission pipeline;

[0024] The shock wave emission controller controls the position of the small Laval nozzle in the shock wave valve core of the shock wave emitter that emits shock waves, or the rotation or oscillation frequency of the shock wave valve core;

[0025] A steady flow control valve is provided at the outlet section of the transmission pipeline. Under the combined action of the hemispherical impeller cup that retreats to recover the shock wave and the shock wave buffer connected in the buffer flow channel, the shock wave is recovered and then flows out smoothly from the oil outlet flow channel of the steady flow control valve.

[0026] The shock wave emission controller controls the position of the small Laval nozzle in the shock wave valve core of the shock wave emitter that emits shock waves, or the rotation or oscillation frequency f of the shock wave valve core. Specifically, it includes:

[0027] Select an orthogonal test with 3 factors and 2 levels. Taking the output flow rate at the outlet section of the transmission pipeline as the optimal solution target, the optimal configuration values of the rotation or oscillation frequency f of the shock wave valve core, the pressure P1 set by the main supply pump source, and the hydraulic oil pressure P2 in the starting section of the transmission pipeline are obtained through the orthogonal test method.

[0028] The output flow rate at the outlet section of the transmission pipeline is mainly positively correlated with the amount of oil liquid V carried by each liquid flow shock wave emitted by the shock wave emitter; also, because the air flow shock wave ejected by the rapid expansion of the gas in the high-pressure gas chamber in the shock wave emitter pushes the diaphragm, and the diaphragm bulges the hydraulic oil in the liquid chamber outwards as a liquid flow shock wave; and the air flow shock wave is an oscillating shock wave that continuously oscillates between the high-pressure gas chamber and the air chamber. The pressure of this shock wave is expressed as a wave equation of positive amplitude exponential decay oscillation:

[0029] P1’×e -kt ×|sinωt|

[0030] In the formula, P1’ is the initial pressure of expansion, k is the decay coefficient with time, t is the oscillation duration, the oscillation circular frequency ω = 2πf, and e is the natural constant;

[0031] Since the process of the air flow shock wave continuously oscillating between the high-pressure gas chamber and the air chamber is an isothermal process, according to the ideal gas state equation:

[0032] pV = nRT = const

[0033] In the formula, p refers to the pressure of the ideal gas, V is the volume of the ideal gas, n represents the amount of gas substance, and T represents the thermodynamic temperature of the ideal gas; R is the ideal gas constant;

[0034] The value of pV is constant, and due to the incompressibility of the oil liquid, the volume of the gas oscillating between the high-pressure gas chamber and the air chamber is related to the shock wave pressure P1’×e -ktIt is inversely proportional to ×|sinωt|, and the phase angle difference is π / 2. Since the volume V of the liquid flow shock wave bulging outward through the diaphragm is equal to the volume bulged by the gas flow shock wave, the volume V of the liquid flow shock wave can also be obtained by integrating the oscillating wave equation with the positive amplitude exponential growth of the agitated gas volume over the action duration Δt:

[0035]

[0036] In the formula, V1 is the initial volume of gas expansion between the high-pressure gas chamber and the air chamber, k is the decay coefficient with time, t is the oscillation duration, the oscillation circular frequency ω = 2πf, e is the natural constant, and Δt is the time when the diaphragm depresses from the air chamber to bulge completely to the maximum volume.

[0037] Due to the adoption of the above technical solution, the beneficial effects obtained by this application are:

[0038] 1. This application relates to a long-distance high-speed transmission system, including a main supply pump source, a discrete shock pump source, a transmission pipeline, and a flow-stabilizing rotary valve; the main supply pump source is connected to the starting section of the transmission pipeline through a lifting pipeline and a first control valve, so that the transmission oil of the main supply pump source flows from the starting section of the transmission pipeline to the outlet section of the transmission pipeline through a pressure difference; through the main supply pump source set in this application, it is possible to continuously supply a high-pressure, stable, and large-flow pressure oil output outward.

[0039] 2. The discrete shock pump source includes a high-pressure accumulator, a shock wave emitter, and a shock wave emission controller; the main supply pump source boosts part of the oil in the fuel tank or the lifting pipeline to a set value, and the boosted 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 pulsating shocks are applied to the oil flowing in the transmission pipeline through the shock wave emitter at a set frequency. The shock wave train formed by the pulsating shocks discretely segments the oil flowing from the starting section to the outlet section in the transmission pipeline into segments of pulsating flow, and each segment of pulsating flow is pushed by the subsequent shock wave, so that the oil in front of the shock wave front is transported to the outlet section of the transmission pipeline at a high speed by rolling; this application sets a discrete shock pump source. The discrete shock pump source utilizes the incompressibility of high-pressure oil to form rapid pressure conduction to detonate the expansion flow of compressed gas; utilizes the compressibility of gas and the spatial volume structure to form the geometric conditions of the gas flow shock wave and the internal power source of the gas flow in the first Laval tube, thereby obtaining the first shock wave power source - the gas flow shock wave; and then utilizes the relatively rigid extrusion of the diaphragm on the oil and the relative compressibility of the liquid flow, and uses the geometric structure of the second Laval tube to form a high-density jet liquid flow shock wave, so that the oil in front of the shock wave front is transported to the outlet section of the transmission pipeline at a high speed by rolling, improving the flow velocity and the volume of the transmitted oil during long-distance transmission.

[0040] The bending radius of a general transmission pipeline shall not be less than 2.5 times the pipe diameter. For a Φ10 pipeline, the pipe clamps are generally one per meter. The conventional pressure difference Δp varies according to different pipeline lengths, bending times and shapes, and pipe diameters, and can at least ensure that the transmitted hydraulic oil is transported to the outlet section of the transmission pipeline according to the conventional pressure difference flow through the transmission pipeline.

[0041] In the pressure difference flow, a basic pressure not lower than 10 MPa can ensure the relative stability of the stiffness of the oil in the transmission pipeline 46, and a discrete flow transmission of a hydraulic quasi-rigid pipeline can be realized (Huang Aiwu, Wang Chengqi, Wang Hongtao. Discrete Flow Transmission and Control of a Hydraulic Quasi-rigid Pipeline [J] Proceedings of the 25th International Conference on Fluid Power and Mechatronics Engineering ICFPMCE 2024:87.). In order to ensure the pressure stability during the transportation from the starting section to the outlet section of the transmission pipeline 46 according to the conventional pressure difference flow, a small pressure difference is selected, so that the transmission pipeline 46 remains in the low-speed laminar flow state of the liquid flow. The characteristic dimension d (pipe diameter) of the transmission pipeline 46 and the dynamic viscosity μ of the oil form a viscous shear vorticity ω = 2μ / d of the pressure difference flow of the oil flowing through the pipe wall acting on the flow velocity v in the pipeline. Due to the rotational action of the viscous shear vorticity ω, rotational momentum will inevitably be generated, and the main motion is still the linear motion along the pipeline axis. Therefore, these rotational momenta must cancel each other out. Therefore, an even number is introduced to maintain symmetry and cancellation, and the pressure difference at both ends of the transmission pipeline at low-speed laminar flow can be obtained:

[0042] ΔP = 16νω = ν×2 4 ω

[0043] It can be concluded from the above formula that the pressure difference head ΔP in the one-dimensional low-speed flow direction is mainly used to provide the rotational shear motion ω to overcome the viscosity of the oil in 4 groups (in 4 directions) of symmetry and the pipe wall and to maintain the flow velocity v in the flow direction.

[0044] It also shows the existence of the rolling rotation motion of the liquid flow in the pressure difference flow under the action of the viscous force, which provides the condition for reducing the pipe wall friction for further utilization of the shock wave to push.

[0045] During the process of the shock wave propagating at the speed of sound, the moving speed of the liquid flow molecular group reaches the maximum, that is, the liquid flow molecular group cannot exceed its maximum moving speed - the speed of sound in the liquid flow (the advancing speed of density propagation collision, related to the hydraulic rigidity, taking K e20 = 1.57 GPa, the density of No. 46 hydraulic oil is ρ = 850 kg / m 3 , and the speed of sound propagation in the oil is c = √K e20 / ρ=√1.57*1000000000 / 850=1359m / s), with such a high collision propagation speed, it is impossible to achieve density uniformity attenuation absorption after one propagation, but it needs to oscillate multiple times in the pipeline, just like the shock wave on the lake surface, and needs the assistance of the shore to oscillate and absorb, so that it can disappear after a long period of back and forth oscillation attenuation in the long transmission pipeline. At such a high speed, it will not be reflected after being received by the receiving end, and there will be no back and forth oscillation attenuation energy loss.

[0046] Therefore, high-speed transmission not only overcomes the friction of the pipe wall under the action of pressure difference laminar flow, but also reduces the energy loss of shock wave oscillation in the pipeline or the damage to the pipeline oscillation due to the timely acceptance of the tail end.

[0047] 3. The steady-flow valve includes a valve body and a valve core arranged in the valve body, the valve core includes a hemispherical impeller cup for recovering shock waves, and the valve body is also provided with an oil inlet channel, an oil outlet channel and a buffer channel connected to the valve core; the oil inlet channel is connected to the outlet section of the transmission pipeline, and a shock wave buffer is connected to the buffer channel; the pulsating impact oil in the transmission pipeline begins to impact the hemispherical impeller cup to rotate after passing through the oil inlet channel, and a part of it enters the buffer channel, among which the pulsating shock wave is partially recovered into the cup due to the retreat of the hemispherical impeller cup, and the remaining shock wave energy is absorbed by the buffer channel through the centrifugal effect of the rotation of the cup, and the pulsating flow part is thrown into the oil outlet channel with the impact rotation of the cup and the centrifugal effect; the shock wave entering the buffer channel is buffered and stabilized by the shock wave buffer and also flows out from the oil outlet channel of the steady-flow valve. The present application sets a steady flow valve, which is set at the tail end of a long-distance high-speed transmission pipeline. For the shock wave of high-speed transmission, the hemispherical impeller cup that recovers the shock wave in the steady flow valve at the tail end of the transmission pipeline receives it like a baseball player catching a baseball. After receiving it, it is not reflected, and there is no energy loss due to the attenuation of oscillation back and forth. Therefore, high-speed transmission not only overcomes the friction of the pipe wall under the action of pressure difference laminar flow, but also reduces the energy loss of shock wave oscillation in the pipeline or the damage to the pipeline oscillation due to the timely reception at the tail end.

[0048] The present application sets up a steady flow valve to further eliminate shock wave pulses, thereby obtaining a hydraulic oil output with more stable flow and pressure, which can serve as a remote hydraulic pump source outlet. BRIEF DESCRIPTION OF THE DRAWINGS

[0049] The drawings described herein are used to provide a further understanding of the present application and constitute a part of the present application. The illustrative embodiments of the present application and their descriptions are used to explain the present application and do not constitute an improper limitation on the present application. In the drawings:

[0050] Figure 1 This is a structural schematic diagram of a hydraulic long-distance high-speed transmission system according to an implementation mode of the present application;

[0051] Figure 2 Schematic diagram of the structure of the main supply pump source of a hydraulic long-distance high-speed transmission system under an embodiment of the present application;

[0052] Figure 3 is Figure 2 Enlarged schematic diagram at position A in

[0053] Figure 4 Schematic diagram of the structure of the discrete impact pump source of a hydraulic long-distance high-speed transmission system under an embodiment of the present application;

[0054] Figure 5 Schematic diagram of the structure of the stable flow control valve of a hydraulic long-distance high-speed transmission system under an embodiment of the present application;

[0055] In the figure,

[0056] 1. Return oil pipe; 2. Main accumulator pump; 21. Main piston; 22. Weight; 23. Driving mechanism; 3. Filter screen; 4. First working chamber; 5. Oil tank; 6. Second working chamber; 7. Delivery pipeline; 8. Input pipeline; 9. First control valve; 10. Second control valve; 11. Auxiliary accumulator; 12. Sub-piston; 13. Filter liquid storage pool; 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 wave generator; 26. Shock wave valve core; 27. Throat; 28. Driving ring; 29. Ring-shaped magnetic strip; 30. High-pressure gas chamber; 31. Explosion impact chamber; 32. Diaphragm; 33. Gas chamber; 34. Liquid chamber; 35. Small Laval nozzle; 36. First fluid channel; 37. Second fluid channel; 38. First Laval tube 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 flow channel; 50. Recovery channel; 51. Oil outlet flow channel. Specific embodiments

[0057] In order to more clearly illustrate the overall concept of the present application, the following will be described in detail by way of examples in conjunction with the accompanying drawings of the specification.

[0058] In the following description, many specific details are set forth in order to fully understand the present application. However, the present application may be implemented in other ways different from those described herein. Therefore, the protection scope of the present application is not limited by the specific embodiments disclosed below.

[0059] In addition, in the description of the present application, it should be understood that the orientation or positional relationship indicated by terms such as "top", "bottom", "inner", "outer", "axial", "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation to the present invention.

[0060] In the present application, unless otherwise clearly specified and defined, terms such as "installed", "connected", "coupled", "fixed", etc. should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or integrated; it can be a mechanical connection, an electrical connection, or a communication connection; it can be directly connected, or indirectly connected through an intermediate medium, and can be the communication inside two elements or the interaction relationship between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0061] In the present application, unless otherwise clearly specified and defined, the first feature being "on" or "under" the second feature can be that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. In the description of this specification, the description referring to terms such as "embodiment", "example", "an embodiment", "example", or "specific example", etc. means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present application. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0062] Embodiment 1

[0063] The present application relates to a long-distance high-speed transmission system, as Figures 1-5 shown, including a main supply pump source, a discrete impact pump source, a transmission pipeline 46, and a steady flow control valve;

[0064] The main supply pump source is connected to the starting section of the transmission pipeline 46 through a lifting pipeline 7 and a first control valve 9, so as to make the transmission hydraulic fluid of the main supply pump source flow from the starting section of the transmission pipeline 46 to the outlet section of the transmission pipeline 46 through a pressure difference;

[0065] The discrete shock pump source includes a boosting device, a high-pressure accumulator, a shock emitter, and a shock emission controller; the shock emission controller controls the rotation or swing of the shock valve core 26 in the shock emitter through a control wire harness connected to the shock emitter; the boosting device boosts a part of the oil in the oil tank 5 or the lifting pipeline 7 to a set value, and the boosted oil is stored in the high-pressure accumulator or transported to the shock emitter; the shock emitter is connected to the transmission pipeline 46, and pulsating shocks are applied to the oil flowing in the transmission pipeline 46 by the shock emitter at a set frequency according to the pressure difference, and the shock train formed by the pulsating shocks discretely segments the oil flowing from the starting section to the outlet section in the starting section of the transmission pipeline 46 into segments of pulsating flow, and each segment of pulsating flow is pushed by the subsequent shock, so that the oil in front of the shock front rolls at a high speed and is transported to the outlet section of the transmission pipeline 46;

[0066] The steady-flow control valve includes a valve body 41 and a valve core 42 arranged in the valve body 41. The valve core 42 includes a hemispherical impeller rotating cup 45 for recovering shocks. The valve body 41 is also provided with an oil inlet flow channel 49, an oil outlet flow channel 51, and a buffer flow channel connected to the valve core 42; the oil inlet flow channel 49 is connected to the outlet section of the transmission pipeline 46, and a shock buffer is connected in the buffer flow channel; the pulsating shock oil in the outlet section of the transmission pipeline 46 enters the buffer flow channel and the oil outlet flow channel in the steady-flow control valve through the oil inlet flow channel 49. After passing through the oil inlet flow channel, the pulsating shock oil starts to impact the hemispherical impeller rotating cup and rotate, and is thrown into the oil outlet flow channel by the impact rotation and centrifugal action of the rotating cup; the shock entering the buffer flow channel is buffered by the shock buffer and then also flows out from the oil outlet flow channel of the steady-flow control valve.

[0067] Through the main supply pump source set in this application, it is possible to continuously supply a high-pressure, stable, and large-flow output outward. By using the incompressibility of high-pressure oil in the discrete shock pump source, rapid pressure conduction is formed to detonate the expansion flow of compressed gas; by using the compressibility of gas and the spatial volume structure, the geometric conditions for forming an air flow shock wave and the internal power source for the air flow in the first Laval tube are formed, so as to obtain the first shock power source - the air flow shock wave; then, by using the relatively rigid extrusion of the diaphragm 32 on the oil and the relative compressibility of the liquid flow, and using the geometric structure of the second Laval tube, a high-density jet liquid flow shock wave is formed, so that the oil in front of the shock front rolls at a high speed and is transported to the outlet section of the transmission pipeline 46, improving the flow velocity of long-distance transmission. Through the setting of the steady-flow control valve, the shock pulse is further eliminated, and a more stable output pressure is obtained. Through the synergistic effect of the main supply pump source, the discrete shock pump source, and the steady-flow control valve, a high-speed and stable flow output over a long distance in the small-diameter transmission pipeline 46 is achieved.

[0068] As a preferred embodiment, the main supply pump source includes an oil return pipe 1, a main accumulator pump 2, an auxiliary accumulator 11, and an output pipeline 47; the main accumulator pump 2 includes a main piston 21, a weight 22, and a driving mechanism 23; the driving mechanism 23 is connected to the main piston 21 through a clutch, and the weight 22 is arranged above the main piston 21; a first working chamber 4 is formed below the main piston 21 located in the main accumulator pump 2, and an oil tank 5 is formed above the main piston 21 located in the main accumulator pump 2. The first working chamber 4 is connected to the starting section of the transmission pipeline 46 through a lifting pipeline 7 and a first control valve 9; when the clutch is engaged, the driving mechanism 23 is used to drive the main piston 21 and the weight 22 to move upward, realizing the lifting of the main piston 21 and the weight 22, so as to pump the oil in the oil tank 5 above the main piston 21 to supplement the first working chamber 4, realizing the oil pumping state; when the clutch is disengaged, the driving mechanism 23 is separated from the main piston 21 and the weight 22, and the main piston 21 and the weight 22 rely on gravity to pressurize the oil in the first working chamber 4, and connect the oil to the starting section of the transmission pipeline 46 through the lifting pipeline 7 and the first control valve 9, so as to realize the oil supply state to the outside.

[0069] 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 a second control valve 10 to achieve 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 to jointly transport the oil to the outside through the output pipeline 47, and can also separately transport the 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 of the main supply pump source to the lifting pipeline 7, the first control valve 9, and the starting section of the transmission pipeline 46 to ensure continuous and stable pressure oil supply.

[0070] When the main supply pump source transports the transmission oil to the starting section of the transmission pipeline 46 in a bypass manner through the lifting pipeline 7 via the first control valve 9, the main accumulator pump 2 moves downward under its own weight, so that the hydraulic oil pressure in the first working chamber 4 is pressed into the lifting pipeline 7. In addition to flowing through the lifting pipeline 7 and the first control valve 9 into the transmission pipeline 46, part of the oil in the lifting pipeline 7 can also enter the second working chamber 6 of the auxiliary accumulator 11; enabling the auxiliary accumulator 11 to be in a standby oil storage state and an auxiliary oil supply state. When the main accumulator pump 2 is in a non-working state, 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.

[0071] Specifically, the main accumulator pump 2 includes a first cylinder block, a main piston 21, a weight 22, a pressure regulating piston 16, and a cover plate 19. Inside the first cylinder block is connected a main piston 21. Above the main piston 21 is provided a weight 22. Inside the main piston 21 is provided an oil storage chamber 15. At the bottom opening of the oil storage chamber 15 in the main piston 21 is connected a pressure regulating piston 16. At the top opening of the oil storage chamber 15 in the main piston 21 is connected a cover plate 19. The main piston 21 divides the first cylinder block into upper and lower parts. The upper part is an oil tank 5, and the lower part is a first working chamber 4 for outputting a stable pressure. The return pipe 1 is also connected to the oil tank 5 in the upper part of the main accumulator pump 2. The oil tank 5 is communicated with the first working chamber 4 in the main accumulator pump 2 through an input pipeline 8 and a first control valve 9. The first control valve 9 can control that the oil in the first working chamber 4 cannot flow back to the oil tank 5 through the input pipeline 8. A centrifugal pump 14 is also provided on the input pipeline 8. The oil outlet of the centrifugal pump 14 is communicated with 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 arranged at the bottom of the oil tank 5 in the upper part of the main accumulator pump 2 through a hose. So that the oil in the oil tank 5 is transported to the first working chamber 4 through the centrifugal pump 14, increasing the oil return force from the oil tank 5 into the first working chamber 4.

[0072] A filter storage pool 13 is also arranged between the first working chamber 4 of the main accumulator pump 2 and the second control valve 10. A filter screen 3 is connected between the filter storage pool 13 and the first working chamber 4. When the main piston 21 is in a working state, the main piston 21 moves downward so that the oil in the first working chamber 4 can enter the filter storage pool 13 through the filter screen 3, and then is output to the auxiliary accumulator 11 or the delivery pipeline 7 through the second control valve 10.

[0073] The auxiliary accumulator 11 includes a secondary piston 12. Below the secondary piston 12 in the auxiliary accumulator 11 is provided a second working chamber 6. The first working chamber 4 is connected to the second working chamber 6 through the second control valve 10 to achieve 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 to jointly transport the oil outward through the delivery pipeline 7, or separately transport the high-pressure oil outward through the delivery pipeline 7 when the main accumulator pump 2 is in a pumping state, or when the main accumulator pump 2 transports oil outward through the delivery pipeline 7, it can assist the main accumulator pump 2 to perform pressure or flow auxiliary adjustment on the pressure fluctuation or flow fluctuation of the delivery pipeline 7 to achieve continuous and stable oil supply output of the pump source.

[0074] A sealing structure is connected between the outer periphery of the main piston 21 and the first cylinder block. The sealing structure includes a sealing tire 17. The sealing structure further includes a support tire 18. The support tire 18 is connected to the main piston 21 and is arranged between the main piston 21 and the first cylinder block. By adjusting the pressure in the sealing tire 17 or the support tire 18, an active gap is formed between the main piston 21 and the first cylinder block when the main piston 21 moves upward, so that the oil in the fuel tank 5 can lubricate the main piston 21 through the active gap, and when the main piston 21 moves downward, the main piston 21 is in sealing contact with the first cylinder block, so that the main piston 21 pressurizes the oil in the first working chamber 4 in the main accumulator pump 2 under the action of gravity.

[0075] As a preferred embodiment, the auxiliary accumulator 11 adopts a bladder accumulator and / or a piston weight 22 accumulator; the stable output pressure of the first working chamber 4 of the main accumulator pump 2 is set as P1, and the set pressure of the second working chamber 6 of the auxiliary accumulator 11 is 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 required time for the main accumulator pump 2 to suck oil is t, then V2 ≥ Q×t.

[0076] As a preferred embodiment, the shock wave emitter includes a shock wave generating body 24, a shock wave valve core 26, a linear motor and a cover plate 19; the shock wave generating body 24 is connected to the cover plate 19, and a shock wave valve core and a linear motor are connected inside the shock wave generating body; a shock wave valve core 26 and a linear motor are connected inside the shock wave generating body 24; the linear motor includes a rotating motor stator annularly arranged in the shock wave generating body 24 to form a driving ring 28, and a rotating motor rotor arranged outside the shock wave valve core 26 to form an annular magnetic strip 29; the shock wave generating body 24 also has a high-pressure gas chamber 30 and a blast chamber 31 which are connected; a diaphragm 32 is arranged in the blast chamber 31, and the blast chamber 31 is separated into a gas chamber 33 and a liquid chamber 34 by the diaphragm 32; the gas chamber 33 is connected to the high-pressure gas chamber 30, and the blast chamber 31 corresponds to a small Laval nozzle 35 inside 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 driving ring 28, so as to release or disperse the oil in the blast chamber 31 into pulsed shock waves.

[0077] The main supply pump source is used to store the oil and energy supplied by the high-pressure oil pump to the blast chamber 31, and buffer or supply the fluctuations of the oil after the blast chamber 31 outputs shock waves.

[0078] 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 cavity 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 cover plate 19 has a shock channel connecting the small Laval nozzles 35 and the transmission pipeline 46; by means of the small Laval nozzles 35 on the shock valve core that rotates or swings, the high-pressure fluid in the small Laval nozzles 35 is suddenly depressurized, resulting in the expansion of the gas in the high-pressure gas chamber and the ejection of a gas shock wave from the throat 27. The gas shock wave pushes the high-pressure fluid in the liquid cavity of the blast chamber along the small Laval nozzles 35 through the diaphragm and ejects a liquid shock wave through the shock channel. Each liquid shock wave impacts and drives the hydraulic oil in the transmission pipeline 46 to accelerate and propagate forward.

[0079] 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 cavity 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 shock valve core 26 that rotates or swings. Each shock wave passes through the shock channel, impacts, and drives the hydraulic oil in front of the shock wave in the transmission pipeline 46 to accelerate and propagate forward.

[0080] 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 cavity 33 of the blast chamber 31, and a first expansion cone 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 to the first conical surface and then 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 and 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 total volume V1 in the high-pressure gas chamber is approximately V 11 + V 12 ≈ 2 / 3πR 3 + 2 / 3πR 3 = 4 / 3πR 3, that is, the volume of a global body with a radius of R. Through the above settings, it is possible to easily calculate and regulate the amplitude and planned number of stepwise pressure adjustments in the aforementioned manner, which is convenient for regulation without damaging the diaphragm. Additionally, after filling the high-pressure gas chamber with the preset high-pressure gas, the gas inlet / outlet is in a closed state, and the liquid chamber of the blast chamber is filled with high-pressure liquid, causing the diaphragm to bulge towards the gas chamber; when the hydraulic oil in the liquid chamber is higher than the outlet pressure of the shock wave channel, when the shock wave spool is driven by the driving mechanism to rotate or swing to connect the injection channel with the conical nozzle 39 and the shock wave channel, the hydraulic oil in the liquid chamber sprays out first, resulting in a sudden decrease in the pressure at the diaphragm (for example, from P1’ = 33 MPa to P2’ = 20 MPa. According to P1’V1’ = P2’V2, assuming the volume of the hemispherical gas in the gas chamber is V’ = V1 / 2, the volume of the gas in the high-pressure gas chamber is V1 = 2V’, and the total volume of the gas when the diaphragm is not compressed is V0 = 3V’, then V1’ is the volume when the diaphragm indents into the gas chamber to make the gas chamber volume 1 / 3V’, that is, V1’ = 1 / 3V’ + 2V’ = 7 / 3V’ = 7 / 6V1 = 7 / 9V0 is the initial volume of expansion; for example, from P1’ = 33 MPa to P2’ = 20 MPa, 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 diaphragm area of the gas chamber expanding forward by the hemisphere radius R), causing the high-pressure gas in the gas chamber and the high-pressure gas chamber to expand and do work externally. Most of the working air flow in the high-pressure gas chamber 30 is compressed to form an accelerating compressed air flow inside the first conical surface and the second conical surface before rushing towards the throat 27, and then is expanded and accelerated after passing through the throat 27 and the first expansion cone surface, thereby forming an impact air flow shock wave on the diaphragm 32 in the gas chamber 33. Since the gas chamber 33 is a hemispherical cavity and the surface area to volume ratio of the sphere is the smallest, the diaphragm 32 must bulge optimally in a spherical shape. Therefore, the air flow shock wave is also a spherical bulge shock wave and continuously oscillates between the high-pressure gas chamber 30 and the gas chamber 33 and impacts the diaphragm 32; this bulge shock wave is expressed as the wave equation of P1’×e -kt ×|sinωt| positive amplitude exponential decay oscillation, where P1’ is the initial pressure of expansion, k is the decay coefficient with time, t is the oscillation duration, and the oscillation circular frequency ω = 2πf’. Through the diaphragm, it impacts the hydraulic oil in the liquid chamber, causing the outflowing hydraulic oil to be compressed and accelerated through the contraction section. The accelerated hydraulic oil forms a liquid flow shock wave after passing through the second Laval nozzle. Due to the isothermal process, pV = nRT is constant and due to the incompressibility of the oil, the volume of the gas oscillating between the high-pressure gas chamber and the gas chamber and the shock wave pressure P1’×e -ktIt is inversely proportional to ×|sinωt|, and the phase angle difference is π / 2. Since the volume V of the liquid flow shock wave bulging outward through the diaphragm is equal to the volume bulged by the gas flow shock wave, the volume V of the liquid flow shock wave can also be obtained by integrating the oscillating wave equation with the positive amplitude exponential growth of the agitated gas volume over the action duration Δt:

[0081] Volume of the liquid flow shock wave

[0082] In the formula, V1 is the initial volume of the gas expansion between the high-pressure gas chamber and the air cavity, k is the decay coefficient with time, t is the oscillation duration, the oscillation circular frequency ω = 2πf, e is the natural constant, and Δt is the time when the diaphragm depresses from the air cavity to bulge completely to the maximum volume.

[0083] The liquid flow shock wave propagates forward along the oil in the output pipeline. Under the reaction of the liquid cavity diaphragm, the gas flow shock wave in the air cavity 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 sound speed in the oil. Therefore, during the duration when the driving mechanism drives the shock valve core to rotate or swing so that the injection channel is connected to the conical nozzle 39 and the shock channel, due to the very high oscillation frequency f, during the process when the diaphragm depresses from the air cavity to bulge completely into a spherical surface, it is impacted by the oscillating gas flow shock wave multiple times. Furthermore, the diaphragm also impacts the outflowing liquid flow shock wave multiple times. In this way, it is beneficial to the accumulation of the thickness δ of the liquid flow shock wave skin, and the intensity of the shock wave increases, so that the liquid flow shock wave carries more liquid density and momentum, and promotes large changes in the flow parameters in front of the shock wave front, such as pressure rise and flow rate acceleration, which is conducive to the rapid discrete transmission of the liquid flow in the long-distance pipeline with diameter d;

[0084] Volume of the liquid flow shock wave During the duration when the driving mechanism drives the shock valve core to rotate or swing so that the injection channel is connected to the conical nozzle 39 and the shock channel, within the process Δt when the diaphragm depresses from the air cavity to bulge completely into a spherical surface, a single liquid flow shock wave skin accumulates continuously. After accumulating to the size of an inverted volume like a half-spherical onion from the outside to the inside, it expands in the shock channel into a spherical shock wave with layers stacked like the outer skin of a half-onion being thin and the inner skin being thick, bulging forward. The pressure in front is P2 in the pipeline, such as P2 = 20 MPa, and the initial pressure P1 in the explosion chamber behind, such as P1 = 33 MPa. Since the oil in the explosion chamber overflows and also reduces to the intensity balanced with the pressure of the air cavity and the pipeline, then P1×e -kt ×|sinωt|≤P1×e -kΔt= P2 ≈ 20 MPa, from which t = t2 - t0 = Δt = ln(P2 / P1) / (-k) (where the starting time t0 = 0) can be calculated. In front of the shock wave is the pressure P2 in the pipeline, such as P2 = 20 MPa, and the initial pressure P1 in the detonation chamber behind the shock wave, such as P1 = 33 MPa. P1 is also the initial pressure of the gas in the air chamber. Since the oil in the detonation chamber overflows, it also reduces to the strength that balances the pressure between the air chamber and the pipeline. Then:

[0085] P1 × e -kt × |sinωt| ≤ P1 × e -kΔt = P2 ≈ 20 MPa

[0086] From this, it can be calculated that:

[0087] t = t2 - t0 = Δt = (1 / (-k))ln(P2 / P1)

[0088] Assume that the volume of the hemispherical gas in the air chamber is V' = V1 / 2, the volume of the gas in the high-pressure gas chamber is V1 = 2V', and the total volume of the gas when the diaphragm is not compressed is V0 = 3V'. Then V1' is the volume when the diaphragm indents into the air chamber so that the volume of the air chamber is 1 / 3V' = 1 / 6V1, that is, V1' = 1 / 3V' + 2V' = 7 / 3V' = 7 / 6V1 = 7 / 9V0, which is the initial volume of expansion. For example, when it decreases from P1' = 33 MPa to P2' = 20 MPa, 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 the volume of the cylinder formed by the diaphragm area of the air chamber expanding forward and moving the radius R of the hemisphere;

[0089] At the starting time t0 = 0, according to the law of conservation of matter, assume that the volume of the convex hemispherical cup-shaped body compressed by the shock wave is V3, and the density increases to ρ3 = (3 / 4V1) / V3 × ρ 液 , and the speed is that the maximum average value of the molecular cluster movement in the liquid flow is equal to the speed of sound c. From the inertial force F = (3 / 4V1 × ρ 液 ) × c = ρ3 × c × ((3 / 4V1) / Δt), it can be obtained that ρ3 = ρ 液 / Δt, combined with the aforementioned ρ3, we can also 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 in which the shock wave is compressed is compressed; the volume compression ratio (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, a normal shock wave formed in the straight flow channel moves forward, and in front of it is also a strong disturbance compression wave. The change in fluid pressure Δp caused by its disturbance is a finite value. From the perspective of energy conservation, it will not exceed P1 - P2, but it is sufficient to cause significant changes in the flow parameters in front of the shock wave front, such as an increase in pressure and an acceleration of the flow velocity. Therefore, the shock wave pushes the liquid flow in front to accelerate and roll forward along the pipe wall; and 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, which propagates in the form of a wave. The propagation speed is equal to the speed of sound c minus the forward movement speed v of the shock wave. The change in fluid pressure it causes is very small, that is, the change in fluid pressure Δp approaches 0 (almost equivalent to the pressure difference in the local length of the differential pressure flow in the conveying pipeline 46), resulting in a weak change in the flow parameters before and after the disturbance, but it is sufficient to reduce the friction of the pipe wall on the flow direction of the liquid flow behind. Moreover, the suction effect caused by the expansion of the oil liquid behind the shock wave or the inertial movement of the shock wave will accelerate the attracting flow of the liquid flow to the previous shock wave; in the liquid flow in front of the shock wave, the fluid oil crushed by the shock wave front has an attached wall viscous rotational inertia and is swirled into the rear of the shock wave to form a vortex, and then is pushed by the next incoming shock wave to accelerate and roll, thereby reducing the friction of the pipe wall for the subsequent shock wave, enabling the liquid flow to propagate forward at a high speed almost close to the speed of sound c.

[0090] Because |sinkt| ≤ 1, So, V3 ≤ V1×(k×Δt + C) = 4 / 3πR 3 ×(k×Δt + C), where C is the integration coefficient. Since the amount of oil liquid transported by each shock wave is also 0 at Δt = 0, so C = 0.

[0091] From Δt = (1 / (-k))ln(P2 / P1), we can get that the shock wave 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 sphere radius R of 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, which is the volume of a hemisphere; when the liquid flow shock wave reaches the diameter d of the conveying pipeline 46 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 move uniformly towards the shock wave front at their own sound speed. If the conical circular cross-section of the opening of the second expansion surface is set to be equal to the cross-sectional area of the conveying pipeline, then the pressure difference before and after the molecular clusters inside the shock wave is 0, that is, the acting pressure before the molecular clusters inside the shock wave skin is equal to the acting pressure after the shock wave skin and is equal to the pressure inside the conveying pipeline, which is 20 MPa; then, when P2 / P1 = 20 / 33 and (-ln(P2 / P1)) ≈ 0.5, the density ρ of the shock wave skin is:

[0092] ρ = (ρ 液 ×3 / 4V1) / V3 ≥ (ρ 液 ×πR 3 ) / (4 / 3πR 3 ×(-ln(P2 / P1))) = 3 / 4ρ 液 / (-ln

[0093] (P2 / P1)) ≈ 3 / 2ρ 液

[0094] In the formula, ρ 液 is the density of the liquid, ρ is the density of the shock wave, and R is the radius of the sphere of the high-pressure gas chamber;

[0095] Also, since the molecular clusters inside the shock wave skin move at the highest sound speed of the internal molecules of the oil liquid, although the thickness δ of the liquid flow shock wave skin is small, the compression density is large, that is, ρ ≥ 3 / 2ρ 液 , then:

[0096] (ρ × V3) × c ≥ (V3 × 3 / 4ρ 液 / (-ln(P2 / P1)) ≈ 3 / 2ρ 液 × V3 × c

[0097] The momentum is very large and the impact force is large, resulting in the pressure in front of the shock wave being greater than the liquid flow pressure inside the conveying pipeline. Furthermore, the shock wave pushes the circulating oil liquid in front of the shock wave inside the pipeline to accelerate and roll forward.

[0098] Under the action of the inertial force F, the normal shock wave formed in the straight-through flow channel moves forward. Since the front of the shock wave is a strong disturbance compression wave, the change in fluid pressure Δp caused by its disturbance is finite but large enough to cause significant changes in the flow parameters in front of the shock wave front, such as an increase in pressure and an acceleration of the flow velocity. Therefore, the shock wave pushes the liquid flow in front to accelerate and roll forward along the pipe wall. Also, since the rear of the shock wave is an expansion wave, there is also a small pressure disturbance in the liquid flow behind the shock wave, which propagates in the form of a wave. The change in fluid pressure it causes is very small, that is, the change in fluid pressure Δp approaches 0, resulting in a slight change in the flow parameters before and after the disturbance. However, it is sufficient to reduce the friction of the pipe wall on the flow of the liquid behind. 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. In the liquid flow in front of the shock wave, the fluid oil crushed by the shock wave front has an attached wall viscous rotational inertia and is swirled into the rear of the shock wave to form a vortex, and then is pushed by the next incoming shock wave to accelerate and roll, thereby reducing the friction of the pipe wall for the subsequent shock wave and enabling the liquid flow to propagate forward at a high speed almost close to the speed of sound c.

[0099] As a preferred embodiment, the valve core 42 further includes a rotating shaft 43, a rotating disk 44, and a plurality of hemispherical impeller cups 45. The rotating shaft 43 is connected to the inside of the valve body 41 through a bearing. The rotating disk 44 is fixed on the rotating shaft 43, and a plurality of hemispherical impeller cups 45 are connected at equal intervals to the outer periphery of the rotating disk 44.

[0100] The oil containing the shock wave impacts the hemispherical impeller cup 45 through the oil inlet flow channel 49, causing the cup 45 to drive the valve core 42 to rotate around the rotating shaft 43. And the shock wave rapidly expands and overflows inside the hemispherical impeller cup 45. The overflowing oil is absorbed by the shock wave through the buffer flow channel in the centrifugal direction of the rotation of the hemispherical impeller cup 45. The remaining oil is thrown into the oil outlet flow channel 51 by the impact rotation and centrifugal action of the hemispherical impeller cup 45. The oil after being absorbed by the shock wave through the buffer flow channel flows to the oil outlet flow channel 51 for output.

[0101] Specifically, the stable flow valve includes a valve body 41, a valve core 42, a shock buffer 48 and a sensor; a support groove, a cavity, an oil inlet flow channel 49, a recovery channel 50 and an oil outlet flow channel 51 are formed in the valve body 41, and a bearing is installed in the support groove; the valve core 42 includes a rotating shaft 43, a rotary disk 44 and a plurality of rotating cups 45 arranged in the cavity; both ends of the rotating shaft 43 are connected to the 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 the axis, and a plurality of rotating cups 45 are connected to the outer periphery of the rotary disk 44 at equal intervals; the sensor is arranged outside the cavity where the rotating cups 45 rotate around the envelope of the valve body 41; the axis lines of the oil inlet flow channel 49 and the oil outlet flow channel 51 are collinear and tangent to the movement track of the center of the rotating cup 45; the opening direction of the rotating cup 45 at the tangent point faces the oil inlet flow channel 49, a recovery channel 50 is opened along the radial direction of the valve core 42 at the tangent point, and the shock buffer 48 is arranged at the bottom of the recovery channel 50; the oil liquid containing shock waves impacts the rotating cup 45 through the oil inlet flow channel 49, so that the rotating cup 45 drives the valve core 42 to rotate around the rotating shaft 43, and the shock waves rapidly expand and splash out in the rotating cup 45, and the splashed oil liquid enters the recovery channel 50 under the centrifugal action of the rotation of the rotating cup 45, and the shock wave energy of this part of the oil liquid is absorbed by the shock buffer 48 at the bottom of the recovery channel 50. A part of the remaining oil liquid in the rotating cup 45 is thrown into the oil outlet flow channel 51 under the impact rotation and centrifugal action of the rotating cup 45, and a part of the oil liquid enters the next impact cycle along with the rotation of the rotating cup 45.

[0102] As a preferred embodiment, a filter 20 is connected in the delivery pipeline 7, and the pressure of the hydraulic oil output in the delivery 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 boosting device boosts a part of the oil liquid in the fuel tank to the set value, the boosting device uses a high-pressure oil pump; when the boosting device boosts a part of the oil liquid in the delivery pipeline to the set value, the boosting device uses a high-pressure oil pump or a boosting oil cylinder.

[0103] The pressure of the delivery pipeline 7 is greater than 7 MPa, preferably 10 MPa.

[0104] Embodiment 2

[0105] This application also relates to a long-distance high-speed transmission method. Based on the above-mentioned long-distance high-speed transmission system, the method specifically includes:

[0106] Step S1: The main supply pump source transports the transmission oil liquid to the starting section of the transmission pipeline 46 in a by-pass manner through the delivery pipeline 7 via the first control valve 9;

[0107] Step S2: The transmission oil liquid is transported to the outlet section of the transmission pipeline 46 according to the conventional pressure difference flow through the transmission pipeline 46; the basic pressure of the outlet section of the transmission pipeline 46 is not lower than 10 MPa;

[0108] In the pressure-difference flow, a base pressure of not less than 10 MPa can ensure relatively stable stiffness of the oil in the transmission pipeline 46, enabling discrete flow transmission of a hydraulic quasi-rigid pipeline (see the paper "Discrete Flow Transmission and Control of a Hydraulic Quasi-rigid Pipeline", authors Huang Aiwu, Wang Chengqi, Wang Hongtao [J] Proceedings of the 25th International Conference on Fluid Power and Mechatronics Engineering ICFPMCE 2024). To ensure pressure stability during the conventional pressure-difference flow from the starting section to the outlet section of the transmission pipeline 46, a small pressure difference is selected, so that the transmission pipeline 46 remains in the low-speed laminar flow state of the liquid. For the pressure-difference flow in which the characteristic dimension d (pipe diameter) of the transmission pipeline 46 and the dynamic viscosity μ of the oil form a viscous shear vorticity ω = 2μ / d of the oil flowing through the pipe wall acting on the flow velocity v in the pipeline, due to the rotational action of the viscous shear vorticity ω, rotational momentum will inevitably be generated, and the main motion is still the linear motion along the pipeline axis. Therefore, these rotational momenta must cancel each other out. Thus, an even number is introduced to maintain symmetry and cancellation, and the pressure difference at both ends of the transmission pipeline 46 during low-speed laminar flow can be obtained:

[0109] ΔP = 16νω = ν×2 4 ω

[0110] It can be obtained from the above formula that the pressure-difference head ΔP in the one-dimensional low-speed flow direction is mainly used to provide the shear rotation motion ω to overcome the viscosity of the oil in 4 groups (in 4 directions) of symmetry and the pipe wall and to maintain the flow velocity v in the flow direction.

[0111] It also shows the existence of the rolling rotation motion of the liquid flow in the pressure-difference flow under the action of viscous force, which provides conditions for reducing the pipe wall friction for further utilization of shock wave propulsion.

[0112] Step S3: The straight section part of the starting section of the transmission pipeline 46 is connected to the shock wave emitter. The shock wave emission controller controls the rotation or swing of the shock wave spool in the shock wave emitter through the control wire harness connected to the shock wave emitter, so that the shock wave emitter emits shock wave liquid flow at a set frequency and pulsates and impacts the oil in the straight section part of the starting section of the transmission pipeline 46. The shock wave liquid flow assists in pushing the oil transported in the transmission pipeline by the conventional pressure-difference flow to overcome the frictional force of the pipe wall on the flow, so that the oil at the front end of the shock wave liquid flow is transported at high speed to the outlet section of the transmission pipeline 46;

[0113] Step S4: The shock wave emission controller controls the position of the small Laval nozzle 35 in the shock wave spool of the shock wave emitter that emits shock waves or the rotation or swing frequency of the shock wave spool 26;

[0114] Step S5: A steady flow control valve is set at the outlet section of the transmission pipeline 46. Under the combined action of the hemispherical impeller rotary cup that recovers the shock wave and the shock wave buffer connected in the buffer flow channel, the shock wave is recovered and stabilized and then flows out from the oil outlet channel 51 of the steady flow control valve.

[0115] It should be noted that the bending radius of the transmission pipeline 46 is not less than 2.5 times the pipe diameter; the conventional pressure difference Δp varies according to different pipeline lengths, bending times and shapes, and pipe diameters, and can at least ensure that the transmission oil is transported through the transmission pipeline 46 to the outlet section of the transmission pipeline 46 according to the conventional pressure difference flow.

[0116] In step S4, the shock wave emission controller controls the position of the small Laval nozzle in the shock wave valve core of the shock wave emitter or the rotation or swing frequency f of the shock wave valve core, specifically including:

[0117] Select an orthogonal experiment with 3 factors and 2 levels, and use the output flow at the outlet section of the transmission pipeline as the optimal solution target. Obtain the optimal configuration values of the rotation or swing frequency f of the shock wave valve core, the pressure P1 set by the main supply pump source, and the hydraulic oil pressure P2 in the starting section of the transmission pipeline through the orthogonal experiment method.

[0118] For example, factor 1 is the pressure P1 set by the main supply pump source, taking two levels of 33 MPa / 25 MPa. Among them, 33 MPa corresponds to level 1, and 25 MPa corresponds to level 2; factor 2 is the hydraulic oil pressure P2 in the starting section of the transmission pipeline, taking two levels of 10 MPa / 20 MPa. Among them, 10 MPa corresponds to level 1, and 20 MPa corresponds to level 2; factor 3 is the frequency f of emitting shock waves, taking two levels of 10 Hz / 20 Hz. Among them, 10 Hz corresponds to level 1, and 20 Hz corresponds to level 2; obtain the L4(2^3) orthogonal table. The meaning of L4(2^3) is as follows: "L" represents the orthogonal table; the number "4" in the subscript of "L" represents 4 horizontal rows, simply called rows, that is, four experiments need to be done; the exponent "3" in the parentheses represents 3 vertical columns, simply called columns, that is, the maximum number of factors that can be arranged is 3; the number "2" in the parentheses represents that there are only 2 kinds of numbers in the main part of the table, that is, the factors have two levels 1 and 2. The characteristic of the orthogonal table is that the experimental method arranged by it has the characteristics of balanced collocation.

[0119] Through 4 experiments, the obtained L4(2^3) orthogonal table is as follows:

[0120] Table 1 Experimental result table of three factors for four experiments

[0121]

[0122] As can be seen from the above, through 4 experiments, after result analysis, such as experiment 2, select factor 1, the pressure P1 set by the main supply pump source = 33 MPa (level 1), factor 2, the hydraulic oil pressure P2 in the starting section of the transmission pipeline = 20 MPa (level 2), factor 3, the oscillation frequency f = 20 Hz (level 2). Taking the maximum transmission speed and flow as the optimal, as long as experiment 2 is better than other experimental groups, then select the corresponding levels of experiment 2 and solidify them into the experimental program.

[0123] In step S3, both the frequency of the shock wave emitter emitting shock waves and the pressure P1 set by the main supply pump source are related to the air flow shock wave generated by the rapid expansion and ejection of the gas in the high-pressure gas chamber 30 of the shock wave emitter. The air flow shock wave pushes the diaphragm 32, and the diaphragm 32 bulges the hydraulic oil in the liquid chamber 34 outward to form a shock wave liquid flow. The air flow shock wave also continuously oscillates between the high-pressure gas chamber 30 and the gas chamber 33 for the spherical bulging shock wave and impacts the diaphragm 32; this bulging shock wave can be expressed as P1’×e -kt ×|sinωt|, the wave equation of positive amplitude exponential decay oscillation, where P1’ is the initial pressure of expansion, k is the decay coefficient with time, t is the oscillation duration, the oscillation circular frequency ω = 2πf’, through the diaphragm, it impacts the hydraulic oil in the liquid chamber, making the outflowing hydraulic oil compressed and accelerated through the contraction section. The output flow rate of the accelerated hydraulic oil through the second Laval nozzle and the outlet section of the transmission pipeline is mainly positively correlated with the volume V of the oil carried by each liquid flow shock wave emitted by the shock wave emitter. Also, because the air flow shock wave generated by the rapid expansion and ejection of the high-pressure gas in the shock wave emitter pushes the diaphragm, the diaphragm bulges the hydraulic oil in the liquid chamber outward into a liquid flow shock wave, and the air flow shock wave is an oscillating shock wave that continuously oscillates between the high-pressure gas chamber and the gas chamber. The pressure of this shock wave is expressed as the wave equation of positive amplitude exponential decay oscillation:

[0124] P1’×e -kt ×|sinωt|

[0125] In the formula, P1’ is the initial pressure of expansion, k is the decay coefficient with time, t is the oscillation duration, the oscillation circular frequency ω = 2πf, and e is the natural constant;

[0126] Since the process of the air flow shock wave continuously oscillating between the high-pressure gas chamber and the gas chamber is an isothermal process, according to the ideal gas state equation:

[0127] pV = nRT = const

[0128] In the formula, p refers to the pressure of the ideal gas, V is the volume of the ideal gas, n represents the amount of gas substance, and T represents the thermodynamic temperature of the ideal gas; R is the ideal gas constant;

[0129] Due to the incompressibility of the oil, the volume of the gas oscillating between the high-pressure gas chamber and the gas chamber is inversely proportional to the shock wave pressure P1’×e -kt ×|sinωt|, with a phase angle difference of π / 2. Since the volume V of the liquid flow shock wave bulged outward by this shock wave through the diaphragm is equal to the volume bulged by the air flow shock wave, and because pV = const, the volume V of the liquid flow shock wave can also be obtained by integrating the positive amplitude exponential growth oscillation wave equation of the oscillating gas volume over the action duration Δt:

[0130] The volume of the liquid flow shock wave

[0131] In the formula, V1 is the initial volume of the gas expansion between the high-pressure gas chamber and the air cavity, k is the decay coefficient with time, t is the oscillation duration, the oscillation circular frequency ω = 2πf, e is the natural constant, and Δt is the time for the diaphragm to sink from the air cavity to fully bulge to the maximum volume.

[0132] Specifically, the air flow shock wave impacts the hydraulic oil in the liquid cavity 34 through the diaphragm 32, causing the outflowing hydraulic oil to be compressed and accelerated through the contraction section. The accelerated hydraulic oil forms a shock wave liquid flow, and the shock wave liquid flow propagates along the transmission direction of the transmission pipeline 46. The air flow shock wave in the air cavity 33 is reflected back to the high-pressure gas chamber 30 to form an oscillating shock wave under the reaction of the diaphragm 32 in the liquid cavity 34. During the process of the diaphragm 32 sinking from the air cavity 33 to fully bulging into a spherical surface, it is impacted by the oscillating shock waves of the air flow shock wave multiple times. Furthermore, the diaphragm 32 also impacts the outflowing shock wave liquid flow multiple times, causing the liquid flow shock wave to carry more liquid density.

[0133] Through the diaphragm, the hydraulic oil in the liquid cavity is impacted, causing the outflowing hydraulic oil to be compressed and accelerated through the contraction section. The accelerated hydraulic oil forms a liquid flow shock wave through the second Laval nozzle; due to the isothermal process, pV = nRT is constant, and due to the incompressibility of the oil, the volume of the gas oscillating between the high-pressure gas chamber and the air cavity is inversely proportional to the shock wave pressure P1’×e -kt ×|sinωt|, with a phase angle difference of π / 2. Since the volume V of the liquid flow shock wave bulging outwards through the diaphragm by this shock wave is equal to the volume of the air flow shock wave bulging out, the volume V of the liquid flow shock wave can also be obtained by integrating the oscillating wave equation of the positive amplitude exponential growth of the volume of the oscillating gas according to the action duration Δt:

[0134] Volume of the liquid flow shock wave

[0135] In the formula, V1 is the initial volume of the gas expansion between the high-pressure gas chamber and the air cavity, k is the decay coefficient with time, t is the oscillation duration, the oscillation circular frequency ω = 2πf, e is the natural constant, and Δt is the time for the diaphragm to sink from the air cavity to fully bulge to the maximum volume.

[0136] The shock wave fluid can propagate forward along the oil fluid in the output pipeline 47. The air flow shock wave in the air chamber 33 is reflected back to the high-pressure air chamber 30 through the first Laval tube under the reaction of the diaphragm 32 in the liquid chamber 34 to form an oscillating shock wave. The oscillation frequency f is approximately (2 / 3R×2) / c (speed of sound). Therefore, during the period when the driving mechanism 23 drives the valve core 42 to rotate or swing so that the injection channel is connected to the conical nozzle 39 and the shock wave channel, due to the very high oscillation frequency f, during the process of the diaphragm 32 sinking from the air chamber 33 to bulging out completely into a spherical surface, it is subjected to multiple oscillating impacts of the air flow shock wave. Furthermore, the diaphragm 32 also impacts the shock wave fluid flowing out multiple times. In this way, it is beneficial to the accumulation of the thickness δ of the shock wave fluid and the increase in the intensity of the shock wave, so that the shock wave fluid can carry more liquid density and momentum, and promote greater changes in the flow parameters in front of the shock wave front, such as an increase in pressure and an acceleration of the flow rate, which is conducive to the rapid discrete transmission of the fluid in the long-distance pipeline, thereby realizing the acceleration of the flow rate of the oil fluid in the transmission pipeline 46.

[0137] The bending radius of a general transmission pipeline is not less than 2.5 times the pipe diameter. For a Φ10 pipeline, the pipe clamps are generally one per meter; the conventional pressure difference Δp varies according to different pipeline lengths, bending times and shapes, and pipe diameters, and can at least ensure that the transmission oil fluid is transported to the outlet section of the transmission pipeline according to the conventional pressure difference flow.

[0138] Estimate the speed of sound propagation c in the oil fluid. The magnitude of the speed of sound c can be calculated through the formula:

[0139] c = √K e / ρ;

[0140] In the formula, K e is the elastic modulus of the oil fluid under a certain pressure in the hydraulic pipeline, with the unit Pa; ρ is the oil fluid density, with the unit kg / m 3 ; c is the speed of sound propagation in the oil fluid, with the unit m / s;

[0141]

[0142] In the formula, p is the pressure of the oil fluid in the closed pipeline, with the unit MPa; K e is the fitted elastic modulus, with the unit of 10 2 MPa; e is the natural constant 2.718;

[0143] Assume that the length L of the transmission pipeline 46 is 140 m, the inner diameter is Φ10 mm, the base pressure p is 20 MPa, the shock wave pressure is 33 MPa, and the pressure change amount Δp = 33 MPa - 20 MPa = 13 MPa. The volume of the oil fluid accommodated in the transmission pipeline 46 is:

[0144] V = 140×1000×π / 4×10×10 = 10990000 / 4 (mm3 ) = 10.99 liters

[0145] From the formula for the bulk modulus of elasticity of the oil Taking the reciprocal, the compression deformation of the oil in the pipeline can be obtained as follows:

[0146] -Δv = V * Δp / K e = 10990000 / 4 (mm 3 ) × 13 MPa / 1.57 GPa ≈ 22.75 ml. At the moment of the shock wave pressure (p + Δp) impact at the end of the 46th pipe of the 5m hydraulic pipeline, the oil volume V in the transmission pipeline hardly changes. The bulk modulus of elasticity K of the No. 46 hydraulic oil e is basically stable between 1.57 GPa and 1.64 GPa, and the bulk modulus of elasticity hardly fluctuates. Choosing 1.57 GPa, for a 10mm hydraulic pipeline, the cross-sectional area of the hydraulic pipeline is 78.5 (mm 2 ), that is, the oil volume compression

[0147] caused by the pipe end pressure impact ΔP = 33 MPa occupies a length L = Δv / 78.5 = 22750 mm 3 / 78.5 mm 2 ≈ 289.8 mm. That is, the longest distance occupied by the 22.75 ml of oil absorbed by the transmission pipeline 46 is 289.8 mm over the entire 140m pipe length - that is, for a shock wave with a capacity of 22.75 ml, the maximum length in a 140m long inner diameter Φ10mm pipeline is 289.8 mm, and the linear average is 289.8 mm / 140m = 0.207%. According to the law of conservation of matter and mass, that is, the compression wave with a sudden change in density at the front end of the hydraulic pipeline, also known as the shock wave, during the subsequent shock operation, the density attenuation per meter in the running direction is about 0.207% (assuming that the shock wave is restricted by the steel pipe in the radial direction of the pipeline and the density does not change. Due to the relative compressibility of the oil, the maximum density attenuation per meter is 0.207%). In fact, this is impossible, and the reasons are as follows:

[0148] During the propagation of the shock wave at the speed of sound, the movement speed of the liquid flow molecular group reaches the maximum, that is, the liquid flow molecular group cannot exceed its maximum movement speed - the speed of sound in the liquid flow (the forward speed of density propagation and collision, related to hydraulic rigidity, taking K e20 = 1.57 GPa, the density of No. 46 hydraulic oil is ρ = 850 kg / m 3 , and the speed of sound propagation in the oil is c = √K e20 / ρ=√1.57*1000000000 / 850=1359m / s), such a high collision propagation speed makes it impossible to achieve density uniformity attenuation absorption after propagation once, but it needs to oscillate multiple times in the pipeline, just like the shock wave on the lake surface, and needs the assistance of the shore to absorb the oscillation, so that it can reach a density attenuation of 0.207% per meter after a period of time in the 140m long inner diameter Φ10mm pipeline, and then the shock wave will disappear. At such a high speed, the hemispherical impeller cup of the receiving end steady flow valve that recovers the shock wave is like a baseball player catching a baseball, and it is not reflected after receiving it, so there is no back and forth oscillation attenuation energy loss. As a result, high-speed transmission not only overcomes the friction of the pipe wall under the action of pressure difference laminar flow, but also reduces the energy loss of shock wave oscillation in the pipeline or the damage to the pipeline oscillation due to the timely acceptance of the tail end.

[0149] Anything not described in this application can be achieved by adopting or drawing on existing technologies.

[0150] The various embodiments in this specification are described in a progressive manner, and the same or similar parts between the various embodiments can be referenced to each other, and each embodiment focuses on the differences from other embodiments.

[0151] The above is only an embodiment of the present application and is not intended to limit the present application. For those skilled in the art, the present application may have various changes and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application should be included in the scope of the claims of the present application.

Claims

1. A long-distance high-speed transmission system, characterized in that: It includes a main supply pump source, a discrete impact pump source, a transmission pipeline and a steady flow valve; The main supply pump source is connected to the starting section of the transmission pipeline through the lifting pipeline and the first control valve, so that the transmission oil of 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; The discrete shock pump source includes a boosting device, a high-pressure accumulator, a shock wave emitter and a shock wave emission controller; the shock wave emission controller controls the rotation or swing of the shock wave valve core in the shock wave emitter by connecting the control harness of the shock wave emitter; the boosting device boosts the pressure of part of the oil in the oil tank or the delivery pipeline to a set value, and the boosted 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 performs pulsating shocks on the oil flowing through the pressure difference in the transmission pipeline at a set frequency, and the shock wave train formed by the pulsating shock discretely divides the oil flowing from the starting section to the outlet section of the transmission pipeline into sections of pulsating flow, and each section of the pulsating flow is pushed by the subsequent shock wave, so that the oil in front of the shock wave front is rolled and delivered to the outlet section of the transmission pipeline at high speed; The steady flow valve includes a valve body and a valve core arranged in the valve body, the valve core includes a hemispherical impeller cup for recovering shock waves, and the valve body is also provided with an oil inlet channel, an oil outlet channel and a buffer channel connected to the valve core; the oil inlet channel is connected to the outlet section of the transmission pipeline, and a shock wave buffer is connected in the buffer channel; the pulsating impact oil of the outlet section of the transmission pipeline enters the buffer channel and the oil outlet channel in the steady flow valve through the oil inlet channel in the steady flow valve, and the pulsating impact oil begins to impact the rotation of the hemispherical impeller cup after passing through the oil inlet channel, and is thrown into the oil outlet channel with the impact rotation of the cup and the centrifugal action; the shock wave entering the buffer channel is buffered and stabilized by the shock wave buffer and also flows out from the oil outlet channel of the steady flow valve.

2. A long-distance high-speed transmission system as claimed in claim 1, characterized in that: The main supply pump source includes an oil return pipe, a main accumulator pump, an auxiliary accumulator and an output pipeline; The main accumulator pump includes a main piston, a weight and a driving mechanism; the driving mechanism is connected to the main piston through a clutch, and the weight is arranged above the main piston; A first working chamber is provided below the main piston in the main accumulator pump, and an oil tank is formed above the main piston in the main accumulator pump. 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 driving mechanism is used to drive the main piston and the weight to move upward, so as to lift the main piston and the weight, so as to extract the oil in the oil tank above the main piston and replenish it into the first working chamber, so as to realize the oil pumping state; when the clutch is disengaged, the driving mechanism is separated from the main piston and the weight, and the main piston and the weight pressurize the oil in the first working chamber by gravity, and connect the oil to the starting section of the transmission pipeline through the lifting pipeline and the first control valve, so as to realize the external oil supply state.

3. A long-distance high-speed transmission system as claimed in claim 2, characterized in that: The auxiliary accumulator adopts an air bag 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 set pressure of the second working chamber of the auxiliary accumulator is P2, then 95% P1≤P2≤P1; the maximum capacity of the second working chamber of the auxiliary accumulator is V2, the maximum flow supplied to the hydraulic equipment is Q, and the time required for the main accumulator pump to be in the oil pumping state is t, then V2≥Q×t.

4. A long-distance high-speed transmission system as claimed in claim 1, characterized in that: The shock wave transmitter comprises a shock wave generator, a shock wave valve core, a linear motor and a cover plate; the shock wave generator is connected to the cover plate, and the shock wave generator is connected to the shock wave valve core and the linear motor; the linear motor comprises a driving ring formed by a rotating motor stator annularly arranged in the shock wave generator, and an annular magnetic strip formed by a rotating motor rotor arranged outside the shock wave valve core; The shock wave generating body also has a connected high-pressure air chamber and an explosion chamber; the explosion chamber is provided with a diaphragm, which divides the explosion chamber into an air chamber and a liquid chamber; the air chamber is connected to the high-pressure air chamber, and the explosion 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 driving ring, so as to release or disperse the oil in the explosion chamber into a pulse shock wave.

5. A long-distance high-speed transmission system as claimed in claim 4, characterized in that: The high-pressure air chamber is provided with a first fluid channel for receiving external charging and discharging gas, and a throat of a first Laval nozzle leading to the air cavity, which converges first and then expands; the explosion cavity is provided with a second fluid channel for receiving external high-pressure fluid and a conical nozzle facing the shock valve core; the shock valve core is provided with a plurality of small Laval nozzles that can correspond to the conical nozzles; The cover plate is provided with a shock wave channel connecting the small Laval nozzle and the transmission pipeline; By rotating or swinging the small Laval nozzle on the shock wave valve core, the high-pressure fluid in the small Laval nozzle is suddenly depressurized, causing the gas in the high-pressure gas chamber to expand and eject an air flow shock wave from the throat. The air flow shock wave pushes the high-pressure fluid in the liquid chamber in the burst chamber through the diaphragm to eject a liquid flow shock wave along the small Laval nozzle through the shock wave channel. Each liquid flow shock wave impacts and drives the hydraulic oil in the transmission pipeline to accelerate and propagate forward.

6. A long-distance high-speed transmission system as claimed in claim 1, characterized in that: The valve core includes a rotating shaft, a rotating disk and a plurality of hemispherical impeller cups; the rotating shaft is connected to the valve body through a bearing, the rotating disk is fixed on the rotating shaft, and the plurality of hemispherical impeller cups are connected to the outer periphery of the rotating disk at equal intervals; The oil containing the shock wave impacts the hemispherical impeller cup through the oil inlet channel, so that the cup drives the valve core to rotate around the rotating axis, and the shock wave expands and overflows rapidly in the hemispherical impeller cup. The overflowed oil absorbs the shock wave through the buffer channel in the centrifugal direction of the rotation of the hemispherical impeller cup; the remaining oil is thrown into the oil outlet channel due to the impact rotation and centrifugal action of the hemispherical impeller cup; the oil after absorbing the shock wave through the buffer channel flows to the oil outlet channel for output.

7. A long-distance high-speed transmission system as claimed in claim 1, characterized in that: A filter is connected to the lifting pipeline, and the hydraulic oil pressure output from 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 of the outlet section of the transmission pipeline; When the booster device boosts the pressure of part of the oil in the oil tank to a set value, the booster device adopts a high-pressure oil pump; when the booster device boosts the pressure of part of the oil in the delivery pipeline to a set value, the booster device adopts a high-pressure oil pump or a booster cylinder.

8. A long-distance high-speed transmission method, based on a long-distance high-speed transmission system according to any one of claims 1 to 7, characterized in that: The methods specifically include: The main supply pump source delivers the transmission oil to the starting section of the transmission pipeline in a bypass manner through the lifting pipeline and the first control valve; The transmission oil is transported to the outlet section of the transmission pipeline according to the conventional pressure difference flow through the transmission pipeline; the basic pressure of the outlet section of the transmission pipeline is not less than 10MPa; The straight section of the starting section of the transmission pipeline is connected to the shock wave transmitter. The shock wave transmitter controller controls the rotation or swing of the shock wave valve core in the shock wave transmitter through the control harness connected to the shock wave transmitter, so that the shock wave transmitter transmits the shock wave liquid flow at a set frequency and performs a pulsating impact on the oil in the straight section of the starting section of the transmission pipeline. The shock wave liquid flow assists in pushing the oil in the transmission pipeline that is transported by the conventional pressure difference flow to overcome the friction of the pipe wall on the flow, so that the oil at the front end of the shock wave liquid flow is rolled and transported to the outlet section of the transmission pipeline at a high speed. The shock wave launch controller controls the position of the small Laval nozzle in the shock wave valve core of the shock wave launcher to launch the shock wave or the rotation or swing frequency of the shock wave valve core; A steady flow valve is set at the outlet section of the transmission pipeline. Under the joint action of the hemispherical impeller cup that recovers the shock wave and the shock wave buffer connected in the buffer flow channel, the shock wave is recovered and stabilized and then flows out from the oil outlet flow channel of the steady flow valve.

9. A long-distance high-speed transmission method as claimed in claim 8, characterized in that: The shock wave launch controller controls the position of the small Laval nozzle in the shock wave valve core of the shock wave launcher to launch the shock wave or the rotation or swing frequency f of the shock wave valve core, specifically including: An orthogonal test with three factors and two levels was selected, and the output flow rate of the outlet section of the transmission pipeline was taken as the optimal solution target. The optimal configuration values ​​of the shock valve core rotation or swing frequency f, the pressure P1 set by the main supply pump source, and the hydraulic oil pressure P2 in the starting section of the transmission pipeline were obtained through the orthogonal test method.

10. A long-distance high-speed transmission method as claimed in claim 9, characterized in that: The output flow rate of the transmission pipeline outlet section is mainly positively correlated with the oil volume V carried by each liquid shock wave emitted by the shock wave transmitter; the airflow shock wave ejected by the rapid expansion of the high-pressure air chamber gas in the shock wave transmitter pushes the diaphragm, and the diaphragm expands the hydraulic oil in the liquid cavity outward as a liquid shock wave; and the airflow shock wave is an oscillating shock wave that continuously oscillates between the high-pressure air chamber and the air cavity. The shock wave pressure is expressed as a wave equation of positive amplitude exponential decay oscillation: P1’×e -kt ×|sinωt| Where P1' is the initial pressure of the expansion, k is the decay coefficient over time, t is the duration of oscillation, the oscillation frequency ω = 2πf, and e is a natural constant; Since the process of the airflow shock wave constantly oscillating between the high-pressure air chamber and the air cavity is an isothermal process, according to the ideal gas state equation: pV=nRT=const In the formula, p refers to the pressure of the ideal gas, V is the volume of the ideal gas, n represents the amount of gas substance, and T represents the thermodynamic temperature of the ideal gas; R is the ideal gas constant; The pV value is constant, and due to the incompressibility of the oil, the volume of the gas oscillating between the high-pressure gas chamber and the air cavity is proportional to the shock wave pressure P1'×e -kt ×|sinωt|, the phase angle difference is π / 2. Since the volume V of the liquid shock wave that bulges outward through the diaphragm is equal to the volume of the air shock wave, the volume V of the liquid shock wave can also be obtained by integrating the oscillating wave equation of the positive amplitude exponential growth of the agitated gas volume according to the action time Δt: Wherein, V1 is the initial volume of the gas expansion between the high-pressure gas chamber and the air cavity, k is the attenuation coefficient over time, t is the oscillation duration, the oscillation circular frequency ω=2πf, e is a natural constant, and Δt is the time it takes for the diaphragm to be sunken in the air cavity and fully expanded to the maximum volume.

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