Integrated intelligent cooling and lubricating system for gearbox of wind generating set

Abstract

The invention relates to the technical field of wind power generation equipment, and discloses an integrated intelligent cooling and lubricating system for a gearbox of a wind generating set, which comprises a main circulating pump set, a heat source distribution subsystem, an adsorption type refrigeration subsystem, a jet flow execution subsystem and an acoustic liquid feedback control subsystem. The main circulating pump set extracts high-temperature lubricating oil, the high-temperature lubricating oil is distributed to the adsorption type refrigeration subsystem through a bistable fluid reversing valve in the heat source distribution subsystem, and refrigeration circulation is driven by oil waste heat. The cooled lubricating oil enters the fluid oscillation nozzle, and the generated pressure pulsation frequency changes along with the viscosity change of the lubricating oil. When the oil temperature rises to enable the pulsation frequency to be matched with the inherent frequency of an acoustic liquid resonance tube in the acoustic liquid feedback control subsystem, the acoustic liquid resonance tube resonates and transmits amplified pressure waves to a control port of the bistable fluid reversing valve, and flow path switching is triggered. The self-adaptive thermal management can be realized without electric control by utilizing the thermal viscosity acoustic liquid coupling characteristic of the fluid.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of wind power generation equipment, in particular to an integrated intelligent cooling and lubricating system for a gear box of a wind turbine generator system. BACKGROUND

[0002] The wind turbine generator system is usually operated in high altitude, offshore or desert and other harsh natural environment, and its gear box, as the core transmission component for converting the low-speed rotation of the impeller into high-speed rotation of the generator, bears extremely high mechanical load and alternating stress. In the energy transmission process, due to the meshing friction of the gear and the operation of the bearing, a considerable part of the mechanical energy will be converted into heat energy, resulting in the increase of the temperature of the lubricating oil. If the heat cannot be removed in time and effectively, the viscosity of the lubricating oil will decrease sharply, causing the rupture of the oil film, and then causing serious faults such as gear pitting, gluing and even bearing burning, which directly affects the utilization rate and service life of the wind turbine generator system.

[0003] At present, the cooling and lubricating system of the gear box of the wind turbine generator system mainly adopts forced air cooling or liquid cooling heat exchange scheme. These traditional schemes generally rely on complex electrical control logic and electromechanical actuators, that is, through the real-time acquisition of oil temperature signals by temperature sensors, the operation of the controller, the driving of electric fans, cooling water pumps and electromagnetic valves or electric regulating valves, and the adjustment of the heat dissipation power. However, this electronic feedback control mode based on sensors to controllers to actuators has reliability problems in the application scene of wind power. The internal environment of the wind turbine generator system cabin is extremely harsh, and is accompanied by long-term high-frequency vibration, large temperature difference and lightning electromagnetic pulse interference factors. Electronic components and precision sensors are prone to signal drift, loose lines or breakdown failure in the above environment, and the actuators with mechanical moving parts such as electromagnetic valves are also prone to jamming failure due to oil pollution or long-term operation. Once any of the above links fails, the entire cooling system will be paralyzed, causing the unit to be forced to shut down for maintenance, resulting in huge loss of power generation.

[0004] In addition, the existing cooling technology also has deficiencies in energy utilization efficiency and self-adaptive ability. The traditional air-cooled radiator can only achieve passive dissipation of heat, and it is difficult to meet the deep cooling demand under the condition of high temperature in summer or continuous overload; while the active refrigeration mode using compressor has good cooling effect, but it will produce huge parasitic power consumption, reducing the net output power of the wind turbine generator system. More importantly, the existing control strategy is mostly based on threshold on-off control or simple PID regulation, which is difficult to accurately follow the rapid fluctuations of the internal thermal load of the gear box in real time, and is prone to problems of cooling lag or excessive cooling leading to high viscosity of the lubricating oil. Therefore, it is a key technical requirement to develop a cooling and lubricating system that can utilize system waste heat, abandon fragile electronic control components, and realize self-adaptive adjustment according to the physical characteristics of the working condition, to improve the operation stability and economy of the wind turbine generator system. SUMMARY

[0005] In view of the deficiencies of the prior art, the application provides an integrated intelligent cooling and lubricating system for a wind turbine gearbox, which solves the problems of low reliability and high failure rate in harsh environments and the inability to utilize waste heat for passive adaptive thermal management due to the dependence on electronic sensors and electrically controlled actuators in the existing cooling system of the wind turbine gearbox.

[0006] To achieve the above object, the application is implemented by the following technical scheme: an integrated intelligent cooling and lubricating system for a wind turbine gearbox, comprising a main circulating pump group, a heat source distribution subsystem, an adsorption refrigeration subsystem, a fluidic actuator subsystem and an acoustic-liquid feedback control subsystem.

[0007] The main circulating pump group is used to extract high-temperature lubricating oil from the gearbox oil sump to provide initial kinetic and thermal energy for the system. The heat source distribution subsystem is in fluid communication with the main circulating pump group, and its core component is a bistable fluid reversing valve. The bistable fluid reversing valve is provided with a main flow inlet, a first control port, a second control port and a first output channel and a second output channel. The valve body utilizes the principle of fluid dynamics to direct the high-temperature lubricating oil to the first output channel or the second output channel according to the pressure signal of the control port without mechanical moving parts.

[0008] The adsorption refrigeration subsystem as an energy conversion unit includes a condenser, a throttling element, an evaporator and a pair of first and second adsorption beds. The heat source channels of the first and second adsorption beds are connected to the first and second output channels of the bistable fluid reversing valve, respectively. The subsystem utilizes the waste heat carried by the high-temperature lubricating oil to drive the internal refrigerant to undergo a desorption-adsorption cycle, thereby generating cold energy at the evaporator to cool the lubricating oil flowing through the evaporator.

[0009] The fluidic actuator subsystem is located downstream of the adsorption refrigeration subsystem and includes a fluid oscillation nozzle. The inlet of the fluid oscillation nozzle is connected to the lubricating oil outlet of the evaporator, and the cooled lubricating oil is sprayed to the key lubrication points of the gearbox in a self-excited oscillation manner. The acoustic-liquid feedback control subsystem constitutes a feedback link of the system and includes an acoustic-liquid resonant tube. The two ends of the acoustic-liquid resonant tube are respectively fluidly connected to the internal pressure pulsation area of the fluid oscillation nozzle and the control port of the bistable fluid reversing valve.

[0010] The present application utilizes the physical mapping relationship between the viscosity-temperature characteristics of lubricating oil and the fluid oscillation frequency to establish a closed-loop control. The pressure pulsation frequency generated by the fluid oscillation nozzle changes with the change of the viscosity of lubricating oil. When the temperature of lubricating oil rises, causing the viscosity to decrease, the pressure pulsation frequency rises. When the frequency matches the natural frequency of the acoustic-liquid resonant tube, the acoustic-liquid resonant tube resonates fluid acoustically, transmits the amplified pressure wave to the control port of the bistable fluid directional valve, and triggers the flow path switching.

[0011] In a further technical solution, the bistable fluid directional valve works on the principle of wall attachment effect. Its structure includes a power nozzle, an interaction area and a flow splitting wedge. The power nozzle accelerates the high-temperature lubricating oil to form a jet; the interaction area is surrounded by a first side wall and a second side wall with a predetermined bias and an inclination angle, so that the jet adheres to one of the side walls; the flow splitting wedge separates the jet into the corresponding output channels. The first control port and the second control port are opened at the starting segment of the side wall, and the flow direction switching is realized by injecting control fluid to destroy the wall attachment effect.

[0012] The adsorption refrigeration subsystem automatically circulates the refrigerant through a refrigerant flow control valve group. The valve group includes a first exhaust check valve, a second exhaust check valve, a first suction check valve and a second suction check valve. The refrigerant vapor ports of the first and second adsorption beds are connected to the condenser inlet through the exhaust check valves, and to the evaporator outlet through the suction check valves. The condenser outlet is connected to the evaporator inlet through a liquid accumulator and a throttling element, forming a closed loop. When the bistable fluid directional valve is turned on to a certain output channel, the corresponding adsorption bed is in a heating and desorption state, releasing refrigerant vapor to the condenser; the other adsorption bed is in a natural cooling and adsorption state, absorbing refrigerant vapor from the evaporator.

[0013] The fluid oscillation nozzle is provided with an oscillation chamber and symmetrically arranged first and second internal feedback channels inside. When the fluid flows in the oscillation chamber, part of the fluid enters the internal feedback channels and forms a feedback pressure wave at the nozzle inlet, forcing the main flow beam to periodically swing left and right. The acoustic-liquid resonant tube is connected to the internal feedback channels to obtain the pressure pulsation signal.

[0014] In the present application, the oscillation frequency of the fluid oscillation nozzle is determined based on the viscosity-temperature characteristics of lubricating oil and the fluid dynamics relationship. The kinematic viscosity of lubricating oil changes with temperature according to the Vogel-Fulcher-Tammann model, while the oscillation frequency of the nozzle changes with the Reynolds number. The Reynolds number is determined by the flow rate, the hydraulic diameter of the nozzle and the real-time kinematic viscosity. Temperature rise causes viscosity to decrease, which in turn causes the oscillation frequency to rise.

[0015] The acoustic liquid resonant tube is configured as a hydraulic transmission line with a predetermined length, which is designed according to a preset switching temperature point of the system, so that when the lubricating oil temperature reaches the preset switching temperature point, the oscillation frequency of the fluid oscillation nozzle is equal to the acoustic fundamental frequency resonance frequency of the acoustic liquid resonant tube. In the resonance state, the pressure gain at the output end of the acoustic liquid resonant tube is sufficient to overcome the switching pressure threshold of the bistable fluid directional valve.

[0016] Preferably, the acoustic liquid feedback control subsystem includes a first acoustic liquid resonant tube and a second acoustic liquid resonant tube connected to the pressure extraction points on both sides of the nozzle and the control ports on both sides of the bistable fluid directional valve, respectively. The two alternately transmit pressure pulse signals to drive the bistable fluid directional valve to reciprocally switch between the two output channels.

[0017] The present application also has the characteristics of self-adaptive adjustment of switching period according to thermal load. The flow path switching period of the bistable fluid directional valve is determined by the rate of change of the thermal physical properties of the lubricating oil flowing through the fluid oscillation nozzle. When the increase of the gearbox input thermal load causes the temperature of the lubricating oil to rise at an increased rate, the frequency of the pressure pulsations generated by the fluid oscillation nozzle increases at a rate synchronized with time, so that the inherent frequency of the acoustic liquid resonant tube is reached in a shorter time, triggering resonance and shortening the flow path switching period, to increase the average refrigeration power.

[0018] The present application provides an integrated intelligent cooling and lubrication system for a wind turbine gearbox, which has the following beneficial effects: 1、The present application uses a bistable fluid directional valve, a fluid oscillation nozzle and an acoustic liquid resonant tube to form a pure fluid control logic circuit, completely replacing the traditional electromagnetic valve, electronic temperature sensor and control chip. This structure without electrical components and mechanical moving parts effectively avoids the problems of electronic component aging, electromagnetic failure or mechanical fatigue jamming that are prone to occur in wind turbine under high altitude, strong electromagnetic interference and long-term vibration environment, realizes intrinsic safety control and greatly reduces the maintenance cost and failure rate of the system.

[0019] 2、The absorption refrigeration subsystem in the present application is configured to directly use the waste heat in the gearbox lubricating oil as a driving heat source to convert low-grade heat energy into refrigeration potential energy. Compared with the traditional vapor compression refrigeration, this system does not need to consume additional electrical energy to drive the compressor, but only needs to use the excess pressure of the main oil pump to maintain operation, realizes cascade utilization of energy while completing deep cooling of the lubricating oil, and improves the overall energy efficiency ratio of the unit.

[0020] 3、The application utilizes the coupling mechanism between the viscosity-temperature characteristics of lubricating oil and the resonant frequency of acoustic resonance, and establishes a closed-loop feedback control without algorithm participation. When the oil temperature rises rapidly due to the increase of the heat load of the gearbox, the jet frequency can drift to the resonance point faster to trigger the flow path switching, thereby automatically shortening the refrigeration cycle period and outputting more average cooling capacity. This passive adaptive adjustment mechanism ensures that the cooling power can follow and match the actual working condition requirements of the gearbox in real time, avoiding overcooling or undercooling. BRIEF DESCRIPTION OF DRAWINGS

[0021] Figure 1 It is a schematic diagram of the overall core architecture of the system of the application. Figure 2 It is a logical diagram of the fluid oscillation nozzle structure of the application. Figure 3 It is a system working timing and adaptive adjustment logic flow chart of the application. DETAILED DESCRIPTION

[0022] The technical solutions in the embodiments of the application will be described in detail below with reference to the drawings in the specification of the application. Obviously, the described embodiments are only a part of the embodiments of the application, not all. Based on the embodiments in the application, all other embodiments obtained by those skilled in the art without creative labor are within the scope of protection of the application.

[0023] Referring to the drawings in the specification of the application, Figure 1 The application provides a wind turbine generator set gearbox integrated intelligent cooling and lubricating system 100 based on thermal flow coupling self-excitation feedback, which is configured in the lubricating circuit of the gearbox 200 of the wind turbine generator set.

[0024] The system 100 mainly includes: a main circulating pump set 110, a heat source distribution subsystem 300, an adsorption refrigeration subsystem 400, a jet execution subsystem 500, and an acoustic liquid feedback control subsystem 600. Each subsystem is physically connected through high-pressure resistant fluid pipelines to form a closed fluid circulation loop.

[0025] The inlet of the main circulating pump set 110 is in fluid communication with the oil sump of the gearbox 200, and is used to extract high-temperature lubricating oil carrying the waste heat of the gearbox operation. The high-temperature lubricating oil is defined as the driving working medium The outlet of the main circulating pump set 110 is connected to the inlet of the precision filter 120, and the outlet of the precision filter 120 is connected to the power inlet end of the heat source distribution subsystem 300 through a pipeline.

[0026] The core component of the heat source distribution subsystem 300 is a bistable fluidic diverter valve 310. The bistable fluidic diverter valve 310 is provided with a main flow inlet 311 connected to the outlet of the precision filter 120. The bistable fluidic diverter valve 310 is also provided with a first output channel 314 and a second output channel 315. The first output channel 314 is connected to the heat exchange inlet of the first adsorption bed 410 of the adsorption refrigeration subsystem 400; the second output channel 315 is connected to the heat exchange inlet of the second adsorption bed 420 of the adsorption refrigeration subsystem 400.

[0027] The bistable fluidic diverter valve 310 also includes a first control port 312 and a second control port 313. The first control port 312 and the second control port 313 are symmetrically arranged on both sides of the throat region downstream of the main flow inlet 311. The control ports are used to receive external pressure pulse signals to change the driving working fluid The flow path inside the bistable fluidic diverter valve 310 is switched between flowing to the first output channel 314 or flowing to the second output channel 315.

[0028] The adsorption refrigeration subsystem 400 includes a pair of first adsorption bed 410 and second adsorption bed 420, and a refrigerant circulation loop composed of a condenser 430, a throttling valve 440 and an evaporator 450. The adsorption bed is filled with adsorbent, and the phase change medium circulating inside the adsorption refrigeration system is defined as refrigeration working fluid .

[0029] The first adsorption bed 410 and the second adsorption bed 420 each have a heat source channel and a refrigerant channel. The heat source channel is connected to the output channel of the bistable fluidic diverter valve 310, allowing the driving working fluid to flow through to provide the heat energy required for desorption. The driving working fluid After flowing through the adsorption bed and releasing heat, it converges to the circuit 130 and returns to the low-speed stage lubrication point of the gearbox 200 or the oil sump.

[0030] The evaporator 450 is provided with a cooled fluid channel. The inlet of the channel is connected to the lubricating oil supply pipeline, and the outlet is connected to the jet execution subsystem 500. In the evaporator 450, the refrigeration working fluid undergoes phase change evaporation, absorbs the heat of the lubricating oil flowing through the cooled fluid channel, and produces low-temperature lubricating oil.

[0031] For the driving working fluid provided to the adsorption bed, the heat input rate is defined by the following formula: ; where, represents the heat input power of the desorption process of the adsorption bed, in watts (W). This indicates the driving working fluid flowing through the heat source channel of the adsorption bed. Mass flow rate, expressed in kilograms per second (kg / s); Indicates the driving working medium Specific heat capacity at constant pressure, expressed in joules per kilogram Kelvin (J / (kg·K)). Indicates the driving working medium The temperature when entering the heat source channel of the adsorption bed, in Kelvin (K). Indicates the driving working medium The temperature at which the adsorption bed heat source flows out, expressed in Kelvin (K).

[0032] The jet actuation subsystem 500 includes at least one fluid oscillation nozzle 510. The fluid oscillation nozzle 510 is arranged above the gear meshing area of ​​the high-speed shaft or intermediate shaft of the gearbox 200. The fluid inlet 511 of the fluid oscillation nozzle 510 is connected to the outlet of the cooled fluid passage of the evaporator 450 and receives low-temperature lubricating oil. The jet outlet 513 of the fluid oscillation nozzle 510 faces the gear meshing surface.

[0033] The fluid oscillation nozzle 510 has a self-excited oscillation chamber and an internal feedback flow channel 512. Low-temperature lubricating oil creates periodic pressure pulsations and flow oscillations within the fluid oscillation nozzle 510. The fluid oscillation nozzle 510 is configured to generate pressure waves of a frequency based on the kinematic viscosity of the fluid passing through it.

[0034] The acoustic-fluid feedback control subsystem 600 includes an acoustic-fluid resonator 610. One end of the acoustic-fluid resonator 610 is fluidly connected to the internal feedback channel 512 of the fluid oscillation nozzle 510 or the pressure outlet of the oscillation chamber, and the other end is fluidly connected to the first control port 312 or the second control port 313 of the bistable fluid reversing valve 310.

[0035] The acoustic-liquid resonator 610 is a section with a predetermined length A rigid conduit with a predetermined inner diameter is provided. This conduit is filled with lubricating oil and forms a hydraulic transmission line. The acoustic-hydraulic resonant tube 610 is configured to transmit the pressure pulsation signal generated by the fluid oscillation nozzle 510 to the bistable fluid directional valve 310.

[0036] When the system is running, the oscillation frequency generated by the fluid oscillation nozzle 510 The frequency varies with the temperature and viscosity of the lubricating oil. The acoustic-liquid resonant tube 610 has an inherent acoustic resonant frequency. When the oscillation frequency of the fluid oscillation nozzle 510 matches the resonant frequency of the acoustic-liquid resonant tube 610, the pressure wave amplitude within the acoustic-liquid resonant tube 610 increases, creating a pressure difference at the control port of the bistable fluid reversing valve 310 sufficient to trigger flow path switching.

[0037] The system 100, through the above connection relationship, utilizes the heat oil discharged by the gearbox 200 to drive the adsorption refrigeration subsystem 400 to work, the low-temperature oil generated by refrigeration is transported to the jet execution subsystem 500, and the frequency signal generated by the jet execution subsystem 500 is reversely controlled by the sound-liquid feedback control subsystem 600 to control the flow path switching of the heat source distribution subsystem 300, so that a heat flow coupling closed-loop control system without an external electric control unit is formed.

[0038] The heat source distribution subsystem 300 of the present application is configured to receive the high-temperature driving working medium from the main circulating pump group 110 , and alternately distribute it to the first adsorption bed 410 or the second adsorption bed 420 based on the fluid dynamics logic. This subsystem does not contain any mechanical moving parts or electromagnetic driving elements.

[0039] The bistable fluid reversing valve 310 includes an integrally formed valve body structure, and the valve body defines a fluid passage network inside. The fluid passage network includes, in sequence along the fluid flow direction: a power nozzle section 311, an interaction zone 316, a flow splitting wedge 317, and two symmetrically arranged output diffusion passages, i.e., a first output passage 314 and a second output passage 315.

[0040] The power nozzle section 311 has a converging geometric shape, and its inlet width is greater than its outlet width. The outlet of the power nozzle section 311 is defined as a nozzle throat 311a. The nozzle throat 311a has a rectangular cross section, and its width-to-height ratio is configured to be greater than 1 to ensure that the driving working medium forms a two-dimensional planar jet.

[0041] The interaction zone 316 is located downstream of the nozzle throat 311a, and is a cavity surrounded by a first side wall 318a, a second side wall 318b, and a top cover and a bottom plate. The first side wall 318a and the second side wall 318b are symmetrically arranged with respect to the central axis of the nozzle throat 311a. A predetermined lateral offset is provided between the starting end of each side wall and the outlet plane of the nozzle throat 311a, and each side wall has a predetermined inclination angle with respect to the central axis.

[0042] The flow splitting wedge 317 is located at the downstream end of the interaction zone 316, and has a sharp wedge structure with its sharp end pointing to the nozzle throat 311a. The flow splitting wedge 317 divides the outlet of the interaction zone 316 into the first output passage 314 and the second output passage 315.

[0043] The first control port 312 and the second control port 313 are respectively formed on the first side wall 318a and the second side wall 318b, and are located close to the offset region at the outlet of the nozzle throat 311a. The first control port 312 is in fluid communication with the first feedback branch of the acoustic-liquid feedback control subsystem 600 through a first control channel; the second control port 313 is in fluid communication with the second feedback branch of the acoustic-liquid feedback control subsystem 600 through a second control channel.

[0044] The mechanism of the wall attachment effect of the bistable fluidic switching valve 310 is described as follows: when the driving working fluid When the main jet is injected into the interaction region 316 at high speed from the nozzle throat 311a, the main jet will entrain the surrounding fluid. Due to the limitation of the surrounding fluid by the side wall (for example, the first side wall 318a), a low pressure region is generated between the main jet and the first side wall 318a, forming a separation bubble or a low pressure vortex. The transverse pressure difference generated by the low pressure region pushes the main jet to and adsorbs it on the first side wall 318a. Once the main jet is attached to the first side wall 318a, the fluid will flow stably along the side wall and enter the first output channel 314 completely, and at this time the second output channel 315 is in a no-flow state. This state is called the first stable state.

[0045] The switching trigger mechanism of the bistable fluidic switching valve 310 is described as follows: when the first control port 312 receives a pressure pulse signal from the acoustic-liquid feedback control subsystem 600, the control fluid is injected into the low pressure separation bubble region between the main jet and the first side wall 318a. The injected fluid increases the pressure of the region, destroys the pressure gradient that maintains the wall attachment effect, and causes the separation bubble to expand and eventually push the main jet away from the first side wall 318a.

[0046] Under the action of inertia, the main jet passes over the tip of the flow splitting wedge 317 and is affected by the entrainment on one side of the second side wall 318b, and quickly attaches to the second side wall 318b and enters the second output channel 315. At this time, the system enters the second stable state. Only when the second control port 313 subsequently receives a new pressure pulse signal, the main jet will switch back to the first stable state again.

[0047] In order to ensure the reliability of switching, the structural parameters of the bistable fluidic switching valve 310 satisfy the following conditions: the side wall inclination angle is set to be between 10 degrees and 15 degrees to ensure the stability of the wall attachment while reducing the control energy required for switching.

[0048] The control port width is set to be between 0.5 and 1.0 times the nozzle throat width to ensure that the control jet has sufficient momentum flux. In the embodiment, the switching threshold of the bistable fluidic switching valve 310 is Defined by the following hydrodynamic relationships: ; in, This indicates the minimum control pressure difference required to trigger the switch; The switching coefficient of the valve body is determined by the side wall offset and tilt angle. Indicates the driving working medium The density; Indicates the driving working medium The flow rate at the nozzle throat 311a.

[0049] Through the above structure and mechanism, the heat source distribution subsystem 300 realizes the logical guidance of the high-temperature oil circuit in response only to the fluid pressure signal without external power input.

[0050] The adsorption refrigeration subsystem 400 of the present invention is configured as a thermodynamic energy conversion unit of the system, utilizing the high-temperature driving working fluid distributed by the heat source distribution subsystem 300. The heat energy drives the internal closed-loop refrigerant. A continuous cycle of adsorption and desorption phase transition occurs, resulting in a cooling effect at the evaporation end that is below the ambient temperature.

[0051] The adsorption refrigeration subsystem 400 includes: a first adsorption bed 410 and a second adsorption bed 420 configured in pairs, a condenser 430, a liquid receiver 435, a throttling element 440, an evaporator 450, and a refrigerant flow control valve assembly 460. The first adsorption bed 410 and the second adsorption bed 420 have the same physical structure, both being shell-and-tube heat exchange reactors. Each adsorption bed includes a high-pressure resistant sealed shell 411 and a tube-fin heat exchanger 412 disposed inside the shell.

[0052] The internal tube-side channels of the tube-fin heat exchanger 412 constitute the driving working fluid. The flow path is the aforementioned heat source channel. A solid adsorbent 413 is filled in the shell-side space between the sealed shell 411 and the tube-fin heat exchanger 412. In this embodiment, the solid adsorbent 413 is selected from microporous silica gel or synthetic zeolite molecular sieves, and the refrigerant is... Deionized water or methanol is selected. Solid adsorbent 413 is cured on the fin surface of tube-fin heat exchanger 412 by sintering or coating process to reduce contact thermal resistance.

[0053] The refrigerant flow control valve assembly 460 consists of four pressure-driven one-way check valves, including: a first discharge check valve 461, a second discharge check valve 462, a first suction check valve 463, and a second suction check valve 464. This valve assembly is used to automatically guide the refrigerant according to the pressure gradient without external power control. steam flow direction.

[0054] The refrigerant vapor ports of the first adsorption bed 410 are in fluid communication with the inlet of the first exhaust check valve 461 and the outlet of the first suction check valve 463, respectively.

[0055] The refrigerant vapor ports of the second adsorption bed 420 are in fluid communication with the inlet of the second exhaust check valve 462 and the outlet of the second suction check valve 464, respectively.

[0056] The outlets of the first exhaust check valve 461 and the second exhaust check valve 462 are connected in parallel to the refrigerant inlet of the condenser 430.

[0057] The inlets of the first suction check valve 463 and the second suction check valve 464 are connected in parallel to the refrigerant outlet of the evaporator 450.

[0058] Regarding the heat-driven desorption process of the adsorption refrigeration subsystem 400 (taking the first adsorption bed 410 as an example): when the bi-stable fluid reversing valve 310 directs the high-temperature driving working medium into the tube-fin heat exchanger 412 of the first adsorption bed 410, heat is transferred to the solid adsorbent 413 through the tube wall and fins. As the temperature rises, the adsorption equilibrium capacity of the solid adsorbent 413 decreases, and the refrigerant adsorbed in the micropores is desorbed by heat and converted into high-temperature high-pressure vapor.

[0059] When the vapor pressure in the first adsorption bed 410 exceeds the pressure in the condenser 430, the first exhaust check valve 461 automatically opens. The refrigerant vapor enters the condenser 430, releases condensation heat to the external environment medium (air or natural wind), and changes phase to condense into a liquid state. The liquid refrigerant flows into the liquid reservoir 435 and then is throttled by the throttling element 440 to enter the evaporator 450.

[0060] Regarding the adsorption refrigeration process of the adsorption refrigeration subsystem 400 (taking the second adsorption bed 420 as an example): at the same time, the second adsorption bed 420 is in a cooled state (no high-temperature oil is introduced, and natural heat dissipation or auxiliary air duct heat dissipation is used). As the temperature of the solid adsorbent 413 decreases, its adsorption capacity recovers. The gas pressure in the second adsorption bed 420 shell rapidly decreases.

[0061] When the pressure is lower than the pressure in the evaporator 450, the second suction check valve 464 automatically opens. Under the driving of the pressure difference, the liquid refrigerant in the evaporator 450 absorbs the heat of the lubricating oil flowing through the evaporator cooling fluid channel, and boils and evaporates. The low-temperature vapor produced is continuously sucked into the second adsorption bed 420, maintaining the low-pressure low-temperature evaporation environment in the evaporator.

[0062] Evaporator 450 is configured as a plate or shell-and-tube heat exchanger. In evaporator 450, the lubricating oil (driving working medium ) to be cooled and the refrigerant working medium under evaporation perform non-contact countercurrent heat exchange. The reduction in the outlet temperature of the lubricating oil is determined by the latent heat of evaporation of the refrigerant working medium and the circulating adsorption amount.

[0063] The transient heat balance process in evaporator 450 follows the following energy conservation relationship: ; wherein, represents the residence mass of the liquid refrigerant working medium in the evaporator; represents the internal energy of the refrigerant working medium ; represents the mass flow rate of the evaporated refrigerant vapor, which is equal to the adsorption rate of the adsorption bed; represents the flow rate of the liquid refrigerant entering the evaporator through throttling; represents the specific enthalpy of the saturated vapor of the refrigerant; represents the specific enthalpy of the saturated liquid of the refrigerant; represents the heat load absorbed from the lubricating oil, i.e., the refrigeration capacity.

[0064] Through the above structure, adsorption refrigeration subsystem 400 converts waste heat into refrigeration effect, providing a low-temperature lubricating oil source with high kinematic viscosity characteristics for subsequent jet execution subsystem 500.

[0065] Jet execution subsystem 500 of the present application is located downstream of adsorption refrigeration subsystem 400 and is configured to have dual functions of actuator and sensor. On the one hand, it sprays the driving working medium after cryogenic treatment to key lubrication points of the gearbox in a dynamic scanning manner; on the other hand, it serves as a kind of fluid logic signal source, generating pressure pulsation signals containing working condition information by using the viscosity-temperature physical characteristics of the driving working medium .

[0066] Fluid oscillation nozzle 510 is a two-dimensional planar fluid element with constant depth, and its internal flow channel structure includes: an inlet contraction section 511, a power nozzle 514, an oscillation chamber 515, an outlet diffusion section 513, and symmetrically arranged first and second internal feedback channels 512a and 512b. The power nozzle 514 is located at the end of the inlet contraction section 511 and has a rectangular cross section. Its function is to accelerate the entering high-pressure driving working medium and form a high-speed jet with momentum flux into the oscillation chamber 515. ​

[0067] The oscillation chamber 515 is a space consisting of an upstream control interaction zone and a downstream mixing zone. At the starting ends of both side walls of the oscillation chamber 515, immediately adjacent to the outlet of the power nozzle 514, a first control port and a second control port are respectively provided. The inlet of the first internal feedback channel 512a communicates with the downstream side of the oscillation chamber 515, and its outlet is connected to the first control port; the inlet of the second internal feedback channel 512b communicates with the other downstream side of the oscillation chamber 515, and its outlet is connected to the second control port.

[0068] The principle of jet sweeping is based on the fluid's wall adhesion effect and negative feedback mechanism. When the driving working fluid... As the fluid exits from the power nozzle 514, random disturbances may occasionally cause it to deflect and adhere to one side wall (e.g., the left side) of the oscillating chamber 515. At this time, some fluid enters the first internal feedback channel 512a on the same side, returning as a pressure wave to the control interaction zone at the nozzle exit. This returning pressure wave acts perpendicularly to the side of the main jet, forcing it to detach from the current wall and switch to the opposite wall (the right side). Subsequently, the fluid enters the second internal feedback channel 512b, generating a reverse feedback pressure wave, triggering the switch again. This cycle repeats, causing the jet exiting the outlet diffuser section 513 to form a fan-shaped angle. It swings continuously from side to side.

[0069] A signal output port 516 is provided on the internal feedback channel (e.g., the first internal feedback channel 512a) of the fluid oscillation nozzle 510 or at the high-pressure point of the oscillation chamber 515. This signal output port 516 is fluidly connected to the acoustic-fluid feedback control subsystem 600 for outputting pressure pulsation signals.

[0070] See attached document Figure 2 In this embodiment, the self-excited oscillation frequency generated by the fluid oscillation nozzle 510 It is not a fixed value, but rather depends on the driving fluid flowing through the nozzle. kinematic viscosity It exhibits a strong nonlinear coupling relationship. This characteristic forms the physical basis for the system's adaptive control.

[0071] First, the driving working fluid (Lubricating oil) kinematic viscosity With temperature The changes follow the Vogel-Fulcher-Tammann relation: ; in, This indicates the driving working fluid entering the fluid oscillation nozzle 510. Real-time temperature; This represents a characteristic constant determined by the type of base oil used in lubricating oil.

[0072] Secondly, the oscillation frequency of the fluidic oscillation nozzle 510 is determined by the fluid dynamics dimensionless numbers Stohal number and Reynolds number. Considering the retarding effect of high viscosity characteristics of lubricating oil on the flow rate in the internal feedback channel, the oscillation frequency is defined as: ; wherein, represents the characteristic Stohal number of the fluidic oscillation nozzle, which depends on the geometry of the nozzle; represents the average flow rate at the power nozzle 514; represents the hydraulic diameter of the power nozzle 514; represents the viscosity correction coefficient related to the internal feedback channel flow resistance; represents the flow regime index; represents the Reynolds number, which is defined as .

[0073] According to the above formula, when the refrigeration subsystem works at high efficiency, so that is reduced, the viscosity increases, resulting in a decrease in the Reynolds number . At this time, the value of the correction term in the brackets in the formula increases, resulting in a decrease in the oscillation frequency . Conversely, when the oil temperature increases, the viscosity decreases, the Reynolds number increases, and the oscillation frequency increases. Therefore, the frequency of the pressure wave output by the fluidic oscillation nozzle 510 directly reflects the current temperature state of the lubricating oil.

[0074] The acoustic-liquid feedback control subsystem 600 of the present application is configured to connect the physical link of the fluidic actuation subsystem 500 and the heat source distribution subsystem 300. Its function is to convert the frequency signal carrying temperature information generated by the fluidic oscillation nozzle 510 into a pressure pulse signal with sufficient energy to drive the bistable fluidic switching valve 310 to switch the flow path. This subsystem uses the principle of fluid acoustic resonance to achieve selective amplification of the frequency signal (band-pass filtering characteristic).

[0075] The acoustic-liquid feedback control subsystem 600 includes at least one acoustic-liquid resonance tube 610. In the preferred embodiment, in order to realize bidirectional alternating control, a first acoustic-liquid resonance tube 610a and a second acoustic-liquid resonance tube 610b are provided.

[0076] One end of the first acoustic-liquid resonance tube 610a is fluidly connected to the first internal feedback channel 512a or the first side signal extraction port of the fluidic oscillation nozzle 510, and the other end is fluidly connected to the first control port 312 of the bistable fluidic switching valve 310.

[0077] One end of the second acoustic liquid resonator tube 610b is fluidly connected to the second internal feedback channel 512b or the second side signal extraction port of the fluidic oscillation nozzle 510, and the other end is fluidly connected to the second control port 313 of the bistable fluidic switching valve 310.

[0078] The acoustic liquid resonator tubes 610a and 610b are configured as rigid conduits (e.g., stainless steel tubes or reinforced hydraulic tubes) with high elastic modulus to minimize signal attenuation caused by tube wall deformation. The inside of the tube is filled with an incompressible driving working fluid From an acoustic point of view, this fluid-filled tube constitutes a hydraulic transmission line.

[0079] The core technical feature of this embodiment is that the geometric size (especially the effective length ) of the acoustic liquid resonator tube is tuned and designed according to the preset switching temperature point of the system.

[0080] The acoustic liquid resonator tube 610, as a distributed parameter system, has a series of inherent acoustic resonance frequencies . For the boundary condition that one end is a pressure wave source (approximately closed) and the other end is connected to a control nozzle (approximately closed or high impedance), its fundamental resonance frequency is determined by the following formula: ; Where, f0 represents the fundamental resonance frequency of the acoustic liquid resonator tube, with the unit of hertz (Hz); c represents the propagation speed (sound speed) of the pressure wave in the driving working fluid , which is related to the bulk modulus and the density of the fluid, i.e. ; L represents the effective acoustic length of the acoustic liquid resonator tube, with the unit of meters (m).

[0081] The working mechanism of the acoustic liquid feedback control subsystem 600 exhibits a frequency-dependent pressure gain characteristic. The pressure gain is defined as the ratio of the pressure amplitude at the control port of the bistable fluidic switching valve to the pressure amplitude output by the fluidic oscillation nozzle.

[0082] ; ; Where, f represents the current oscillation frequency of the fluidic oscillation nozzle 510, which is determined by the real-time viscosity of the driving working fluid α (see the fourth part for details); ζ represents the damping ratio of the system, which is mainly determined by the frictional resistance along the tube.

[0083] The control logic of the system is achieved through the following physical processes: Non-resonant state (hold mode): When the adsorption refrigeration subsystem is in the high-efficiency refrigeration stage, the driving working fluid α has a low temperature and a high viscosity. At this time, the oscillation frequency generated by the fluid oscillation nozzle 510 is lower than the resonance frequency of the acoustic-liquid resonant tube (i.e. ).

[0084] According to the gain formula, the pressure gain at this time is or lower. The pressure pulse amplitude transmitted to the control port of the bistable fluid reversing valve is small, which cannot overcome the wall-attached locking force inside the bistable valve.

[0085] ; wherein, is the switching pressure threshold of the bistable fluid reversing valve. Therefore, the bistable valve remains in the current flow path, continuously supplying heat to the current adsorption bed.

[0086] Resonant state (switching mode): As the adsorption bed tends to be saturated, the refrigeration efficiency decreases, and the driving working fluid temperature gradually rises, and the viscosity decreases. The oscillation frequency of the fluid oscillation nozzle 510 rises accordingly.

[0087] When the temperature rises to the preset switching temperature point, the corresponding oscillation frequency approaches the resonance frequency of the acoustic-liquid resonant tube (i.e. ).

[0088] At this time, the system occurs fluid acoustic resonance, and the pressure gain rises sharply (G ). A high-intensity standing wave pressure peak is formed at the control port of the bistable fluid reversing valve.

[0089] ; This high-pressure pulse instantaneously destroys the wall-attached balance of the main jet of the bistable valve, forcing the main jet to switch to the other output channel, thereby starting the regeneration process of the other adsorption bed, completing the automatic reversing of the refrigeration cycle.

[0090] By setting the length of the acoustic-liquid resonant tube , the target working temperature range of the system can be accurately set without the participation of any electronic sensors or controllers.

[0091] Referring to the accompanying Figure 3The present part will elaborate the complete physical process from start-up to stable operation of the system, as well as the adaptive adjustment mechanism under different gear box thermal load conditions. The system working process of the present invention is a continuous closed-loop process based on the change of fluid thermal physical properties, mainly including the self-starting phase, the first half-cycle running phase, the resonance trigger switching phase and the second half-cycle running phase.

[0092] In the self-starting phase, the main circulating pump group 110 starts to pump the high-temperature driving working medium into the heat source distribution subsystem 300. At this time, due to the inevitable slight geometric asymmetry inside the bistable fluidic reversing valve 310 or the initial turbulent disturbance of the flow field, the main jet entering the power nozzle 311 will randomly adhere to the first side wall 318a or the second side wall 318b. Assuming that the main jet adheres to the first side wall 318a at the initial moment, the driving working medium flows to the first output channel 314, and the system enters the first half-cycle running state.

[0093] In the first half-cycle running phase, the system performs the following thermodynamic and fluid dynamic operations: the high-temperature driving working medium continuously flows through the heat source channel of the first adsorption bed 410 to heat and desorb the internal adsorbent. At the same time, the second adsorption bed 420 is in a natural cooling or auxiliary heat dissipation state, and its internal pressure decreases, causing the refrigerant inside the evaporator 450 to boil and evaporate.

[0094] The driving working medium flowing through the evaporator 450 cooling fluid channel releases heat and its temperature decreases to the preset cryogenic temperature interval. Subsequently, the low-temperature high-viscosity driving working medium enters the jet execution subsystem 500. Since the temperature of the driving working medium is low at this time, according to the aforementioned viscosity-temperature characteristic formula, its kinematic viscosity is at a high value. The fluid oscillation nozzle 510 works under low Reynolds number conditions, and the self-excited oscillation frequency it generates is in the low frequency band.

[0095] At this time, the oscillation frequency is lower than the inherent resonance frequency of the acoustic-liquid resonant tube 610 in the acoustic-liquid feedback control subsystem 600. The acoustic-liquid resonant tube is in a non-resonant transmission state, which attenuates the pressure wave signal or only maintains unit gain. The pressure pulsation amplitude transmitted to the first control port 312 of the bistable fluidic reversing valve 310 is smaller than the switching threshold value of the valve body. Therefore, the main jet of the bistable fluidic reversing valve 310 is fluidically locked at the first side wall 318a, maintaining the current heat source distribution state.

[0096] Upon entering the resonant trigger switching phase, as the first half-cycle continues, the system state gradually changes: the adsorbent in the first adsorption bed 410 is completely desorbed, and the heat utilization rate decreases; simultaneously, the second adsorption bed 420 gradually approaches adsorption saturation, the adsorption rate decreases, causing the evaporation pressure in the evaporator 450 to rise again. Affected by the decrease in refrigeration efficiency, the driving working fluid flowing out of the evaporator 450 and into the fluid oscillation nozzle 510... temperature It has begun to gradually recover.

[0097] temperature The increase leads to the driving working fluid kinematic viscosity The frequency decreases exponentially. Consequently, the fluid velocity inside the fluid oscillation nozzle 510 increases, the wall adhesion switching delay decreases, resulting in an increase in the output oscillation frequency. Gradually increasing.

[0098] When the driving working fluid When the temperature rises back to the system's designed switching critical temperature, the real-time oscillation frequency of the fluid oscillation nozzle 510... The frequency rises to the natural resonant frequency of the acoustic fluid resonator 610. It is consistent with or falls within its high-gain bandwidth (i.e. .

[0099] At this moment, a strong hydroacoustic resonance occurs in the acoustic-fluid feedback control subsystem 600. At the first control port 312, pressure waves superimpose to form a high-amplitude standing wave pressure pulse, the amplitude of which... Exceeding the switching threshold .

[0100] The high-pressure control jet disrupts the low-pressure separation bubbles in the interaction zone of the bistable fluid reversing valve 310, forcing the main jet to detach from the first sidewall 318a, cross the diversion wedge 317, and adhere to the second sidewall 318b. The system instantly completes the flow path switching.

[0101] During the second half of the operating cycle, the heat source logic reverses: high temperature drives the working fluid. The fluid then flows to the second output channel 315, where it begins to heat the second adsorption bed 420 for regeneration. Simultaneously, the first adsorption bed 410 stops heating and begins to cool, switching to adsorption mode and lowering the pressure inside the evaporator 450 again.

[0102] Refrigeration cycle restarts, driving working fluid As the temperature decreases again, the viscosity increases, and the oscillation frequency... Fall back to the low-frequency non-resonant zone. Due to the hysteresis of the bistable fluid reversing valve, the main jet will be steadily maintained at the second side wall 318b until a new reverse control signal triggers.

[0103] Until the desorption of the second adsorption bed 420 is completed and the adsorption saturation of the first adsorption bed 410, the oil temperature rises again, triggering the second acoustic liquid resonant tube 610b to produce resonance, injecting high-pressure pulses into the second control port 313, and the system switches back to the first steady state again. This system has an adaptive thermal balance adjustment mechanism based on the physical constitutive relationship, which is specifically manifested as follows: When the wind turbine gear box 200 is in high load or harsh working conditions, the waste heat generated increases sharply, causing the driving working medium The base oil temperature rises.

[0104] Under high heat load input, the desorption rate of the adsorption bed increases, and the heat load of the evaporator increases, causing the driving working medium The temperature rises faster after cooling (i.e., the derivative of temperature with respect to time Increases).

[0105] This means that the oscillation frequency of the fluid oscillation nozzle 510 Will be faster from low frequency scanning to resonance frequency . As a result, the adsorption and desorption switching period of the system Automatically shortened. The acceleration of the switching frequency increases the amount of refrigerant circulating per unit time, thereby outputting more average refrigeration power to match the external high heat load.

[0106] Conversely, under low load working conditions, the oil temperature rises slowly, the frequency drifts slowly, the switching period is automatically extended, and unnecessary waste of thermal cycles is avoided. The entire adjustment process is completely determined by the physical properties of the fluid's thermal viscous acoustic liquid coupling, without the need for any external sensor detection, electronic calculation or actuator action, achieving an intrinsically safe adaptive thermal management.

Claims

1. An integrated intelligent cooling and lubrication system for a wind turbine gearbox, characterized in that, include: The main circulation pump set is used to pump high-temperature lubricating oil; The heat source distribution subsystem includes a bistable fluid reversing valve, which has a main flow inlet connected to the main circulation pump group, a first and a second control port, and a first and a second output channel. An adsorption refrigeration subsystem includes a condenser, a throttling element, an evaporator, and first and second adsorption beds; the heat source channels of the first and second adsorption beds are respectively connected to the first and second output channels, and the heat energy of the high-temperature lubricating oil is used to drive a refrigeration cycle to cool the lubricating oil flowing through the evaporator; The jet execution subsystem includes a fluid oscillation nozzle, the inlet of which is connected to the lubricating oil outlet of the evaporator for spraying cooled lubricating oil. The acoustic-fluid feedback control subsystem includes an acoustic-fluid resonant tube, the two ends of which are fluidly connected to the internal pressure pulsation region of the fluid oscillation nozzle and the control port of the bistable fluid reversing valve, respectively. The pressure pulsation frequency generated by the fluid oscillation nozzle varies with the viscosity of the lubricating oil. When the frequency matches the natural frequency of the acoustic-liquid resonant tube, the acoustic-liquid resonant tube transmits the amplified pressure wave to the control port to trigger the switching of the bistable fluid reversing valve.

2. The integrated intelligent cooling and lubrication system for a wind turbine gearbox according to claim 1, characterized in that, The bistable fluid directional valve includes: Power nozzles are used to accelerate high-temperature lubricating oil into a jet stream. The interaction zone, located downstream of the power nozzle, is formed by a first sidewall and a second sidewall. The first sidewall and the second sidewall have a predetermined offset and tilt angle relative to the central axis of the power nozzle. The jet is made to adhere to one of the sidewalls and flow by utilizing the wall adhesion effect. A diverter wedge, located downstream of the interaction zone, is used to divide the jet into the first output channel or the second output channel; The first control port and the second control port are respectively opened at the beginning section of the first sidewall and the second sidewall, and are used to inject control fluid that disrupts the wall adhesion effect.

3. The integrated intelligent cooling and lubrication system for a wind turbine gearbox according to claim 1, characterized in that, The adsorption-type refrigeration subsystem also includes: The refrigerant flow control valve group includes a first exhaust check valve, a second exhaust check valve, a first suction check valve, and a second suction check valve. The refrigerant vapor ports of the first adsorption bed and the second adsorption bed are respectively connected to the inlet of the condenser through the first exhaust check valve and the second exhaust check valve. The refrigerant vapor ports of the first adsorption bed and the second adsorption bed are respectively connected to the outlet of the evaporator through the first suction check valve and the second suction check valve. The outlet of the condenser is connected to the inlet of the evaporator via a liquid receiver and the throttling element, forming a closed refrigerant circulation loop.

4. The integrated intelligent cooling and lubrication system for a wind turbine gearbox according to claim 1, characterized in that, The fluid oscillation nozzle is internally equipped with: The oscillation chamber is located downstream of the nozzle inlet; The first internal feedback channel and the second internal feedback channel are symmetrically arranged on both sides of the oscillation chamber; When the fluid flows in the oscillation chamber, a portion of the fluid enters the first internal feedback channel or the second internal feedback channel and forms a feedback pressure wave at the nozzle inlet, forcing the main stream to oscillate periodically left and right in the oscillation chamber. The acoustic-liquid resonator is connected to the first internal feedback channel or the second internal feedback channel.

5. The integrated intelligent cooling and lubrication system for a wind turbine gearbox according to claim 4, characterized in that, The pressure pulsation frequency generated by the fluid oscillation nozzle is determined based on the viscosity-temperature characteristics of the lubricating oil and the relationship with fluid dynamics. The kinematic viscosity of the lubricating oil changes with temperature according to the Vogel-Fulcher-Tammann model; The oscillation frequency of the fluid oscillation nozzle varies with the Reynolds number, which is determined by the flow velocity of the lubricating oil flowing through the nozzle, the hydraulic diameter of the nozzle, and the real-time kinematic viscosity of the lubricating oil. When the temperature of the lubricating oil increases, causing the kinematic viscosity to decrease, the oscillation frequency of the fluid oscillation nozzle increases.

6. The integrated intelligent cooling and lubrication system for a wind turbine gearbox according to claim 5, characterized in that, The acoustic-liquid resonator is constructed as a hydraulic transmission line of a predetermined length; The predetermined length is determined according to the preset switching temperature point of the system, so that when the lubricating oil temperature reaches the preset switching temperature point, the oscillation frequency of the fluid oscillation nozzle is equal to the acoustic fundamental frequency resonance frequency of the acoustic-liquid resonant tube. In the resonant state, the pressure gain at the output end of the acoustic-liquid resonator is sufficient to overcome the switching pressure threshold of the bistable fluid reversing valve.

7. The integrated intelligent cooling and lubrication system for a wind turbine gearbox according to claim 1, characterized in that, The acoustic-liquid feedback control subsystem includes a first acoustic-liquid resonant tube and a second acoustic-liquid resonant tube. The first acoustic-liquid resonant tube connects the first side pressure lead-out point of the fluid oscillation nozzle to the first control port of the bistable fluid reversing valve. The second acoustic-liquid resonator tube connects the second side pressure lead-out point of the fluid oscillation nozzle to the second control port of the bistable fluid reversing valve; The first acoustic-liquid resonator and the second acoustic-liquid resonator alternately transmit pressure pulse signals and drive the bistable fluid reversing valve to switch back and forth between the first output channel and the second output channel.

8. The integrated intelligent cooling and lubrication system for a wind turbine gearbox according to claim 1, characterized in that, The operating mode of the adsorption refrigeration subsystem is configured as follows: When the bistable fluid reversing valve opens the first output channel, the first adsorption bed is in a heating and desorption state, releasing refrigerant vapor to the condenser. Meanwhile, the second adsorption bed is in a natural cooling adsorption state, drawing refrigerant vapor from the evaporator; When the bistable fluid reversing valve opens the second output channel, the second adsorption bed is in a heated desorption state, and the first adsorption bed is in a natural cooling adsorption state.

9. The integrated intelligent cooling and lubrication system for a wind turbine gearbox according to claim 1, characterized in that, It also includes precision filters; The outlet of the main circulation pump set is connected to the inlet of the precision filter; The outlet of the precision filter is split into two paths. The first path is connected to the main flow inlet of the bistable fluid reversing valve as a driving heat source, and the second path is connected to the inlet of the cooled fluid channel of the evaporator as the medium to be cooled.

10. An integrated intelligent cooling and lubrication system for a wind turbine gearbox according to claim 1, characterized in that, The flow path switching cycle of the bistable fluid reversing valve is determined by the rate of change of the thermophysical properties of the lubricating oil flowing through the fluid oscillation nozzle; When the increased thermal load input to the gearbox leads to a faster rate of temperature recovery in the lubricating oil, the rate at which the pressure pulsation frequency generated by the fluid oscillation nozzle increases with time also increases. The pressure pulsation frequency reaches the natural frequency of the acoustic-liquid resonator in a shorter time, thereby triggering the pressure amplification effect of the acoustic-liquid resonator and shortening the flow path switching cycle of the bistable fluid reversing valve.

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