CN113027870A - Independent heat dissipation system of all-terrain armored vehicle and control method thereof - Google Patents
Independent heat dissipation system of all-terrain armored vehicle and control method thereof Download PDFInfo
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- CN113027870A CN113027870A CN202110287856.1A CN202110287856A CN113027870A CN 113027870 A CN113027870 A CN 113027870A CN 202110287856 A CN202110287856 A CN 202110287856A CN 113027870 A CN113027870 A CN 113027870A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/042—Controlling the temperature of the fluid
- F15B21/0423—Cooling
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
- F01P11/14—Indicating devices; Other safety devices
- F01P11/16—Indicating devices; Other safety devices concerning coolant temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D19/00—Axial-flow pumps
- F04D19/002—Axial flow fans
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/004—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by varying driving speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
Abstract
The invention discloses an all-terrain armored vehicle independent heat dissipation system and a control method thereof, and relates to the technical field of special vehicle heat dissipation. The bidirectional closed hydraulic pump device comprises a closed pump, a swash plate direction control valve, a variable piston, a first throttling valve, a second throttling valve, a two-position three-way electro-hydraulic control valve and a shuttle valve, wherein the swash plate direction control valve is used for changing the oil pumping direction of the closed pump, the variable piston is used for adjusting the oil pumping flow of the closed pump, each control current of the bidirectional closed hydraulic pump device has a unique corresponding relation with the working pressure of a system, the corresponding rotating speed of a fan can be correspondingly calculated, the corresponding control current is output according to each cooling medium temperature signal monitored and diagnosed, the dynamic adjustment of the rotating speed of the axial flow fan can be realized, and the control process is very simple.
Description
Technical Field
The invention relates to the technical field of special vehicle heat dissipation, in particular to an all-terrain armored vehicle independent heat dissipation system and a control method thereof.
Background
With the continuous promotion of national energy conservation and emission reduction standards, the heat dissipation system of the special vehicle is gradually converted from an integrated heat dissipation system into an independent heat dissipation system, the rotating speed of the fan is adjusted in real time by monitoring the inlet and outlet temperatures of a water radiator, an intercooler, a hydraulic oil radiator, a torque converter/gearbox oil radiator and a transfer case oil radiator, the dynamic link of the rotating speed of the fan according to the heat dissipation requirements of the vehicle is realized, and the energy conservation and emission reduction effects of the vehicle are promoted.
The independent heat dissipation system in the prior art usually takes an open system as a main part, and the total oil tank is larger, so that the weight of the whole vehicle is increased. The traditional independent heat dissipation system generally adjusts the flow of a fan driving motor through a proportional electromagnetic overflow valve, so that the rotating speed of the fan is controlled, heat dissipation is realized as required, redundant flow in a system loop can only return to an oil tank through overflow, a hydraulic system generates heat, and energy loss is caused. In addition, the conventional heat dissipation system adopts a hydraulic motor to drive an axial flow fan, the efficiency of the fan is low, and the heat dissipation requirement of the system can be met only by increasing a radiator or improving the rotating speed, the diameter and the like of the fan. The problems of large and thick radiator, heavy weight, high noise of the fan and the like are finally caused.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provides an all-terrain armored vehicle independent heat dissipation system and a control method thereof. The closed independent heat dissipation system is adopted, real-time temperature signals can be collected to serve as a control basis, the characteristics of the fan are combined, and the control mode of the motor power/rotating speed is limited by limiting the system pressure, so that the rotating speed of the fan can be adjusted in real time, the requirement of heat dissipation as required is met, and the energy-saving and emission-reducing effects of vehicles are improved.
The purpose of the invention is realized by the following technical scheme:
an independent heat dissipation system of an all-terrain armored vehicle comprises a power take-off device, a bidirectional closed hydraulic pump device, an oil tank, a quantitative hydraulic motor device and an axial flow fan; the bidirectional closed hydraulic pump device comprises a closed pump, a swash plate direction control valve, a variable piston, a first throttle valve, a second throttle valve, a two-position three-way electro-hydraulic control valve and a shuttle valve, wherein two working oil ports of the closed pump are respectively communicated with an oil port A and an oil port B, an oil draining port of the closed pump is communicated with an oil port T, the oil port T is communicated with an oil tank, the swash plate direction control valve is used for changing the oil pumping direction of the closed pump, the variable piston is used for adjusting the displacement of the closed pump, the variable piston comprises a cylinder barrel, a piston rod and a spring, the piston is slidably arranged in the cylinder barrel, the cylinder barrel is divided into a c cavity and a d cavity by the piston, the spring and the piston rod are both arranged in the c cavity, two ends of the spring are respectively connected with the piston and the cylinder barrel, one end of the, the other end of the piston rod penetrates through the cylinder barrel and is connected with a swash plate of the closed pump, the cavity c is communicated with the oil port T, the cavity d is communicated with the oil port T through the second throttle valve, two oil inlets of the shuttle valve are respectively communicated with the oil port A and the oil port B, an oil outlet of the shuttle valve is communicated with a pressure oil port of the two-position three-way electro-hydraulic control valve, a working oil port of the two-position three-way electro-hydraulic control valve is communicated with the cavity d through the first throttle valve, and an oil return port of the two-position three-way electro-hydraulic control valve is communicated with the oil port T; the output shaft of the power taking device is in transmission connection with the power shaft of the closed pump, the quantitative hydraulic motor device comprises a hydraulic motor, the hydraulic motor comprises a working oil port A1 and a working oil port B1, the oil port A and the oil port B are respectively communicated with a working oil port A1 and a working oil port B1 of the hydraulic motor, the output shaft of the hydraulic motor is connected with the input shaft of the axial flow fan, and the oil drainage port of the hydraulic motor is communicated with the oil tank.
The oil supplementing device comprises an oil supplementing pump, a first check valve, a second check valve and an oil supplementing overflow valve, a power shaft of the oil supplementing pump is in transmission connection with a power shaft of the closed pump, an oil suction port of the oil supplementing pump is communicated with the oil tank, a pump oil port of the oil supplementing pump is communicated with an oil inlet of the first check valve, an oil inlet of the second check valve and an oil inlet of the oil supplementing overflow valve, an oil outlet of the first check valve is communicated with the oil port A, an oil outlet of the second check valve is communicated with the oil port B, and an overflow port of the oil supplementing overflow valve is communicated with the oil tank.
Further, an oil absorption filter is arranged between the oil supplementing pump and the oil tank.
Furthermore, the quantitative hydraulic motor device further comprises a flushing valve, wherein the flushing valve comprises a three-position three-way electromagnetic valve and a flushing overflow valve, an O port and a P port of the three-position three-way electromagnetic valve are respectively communicated with the oil port A and the oil port B, an A port of the three-position three-way electromagnetic valve is communicated with an oil inlet of the flushing overflow valve, and an overflow port of the flushing overflow valve is communicated with an oil drainage port of the hydraulic motor.
And the oil drainage port of the hydraulic motor, the overflow port of the oil supplementing overflow valve and the oil port T are communicated with the oil tank through the cooler.
Further, the device also comprises a controller which is respectively and electrically connected with the swash plate direction control valve and the two-position three-way electrified liquid control valve.
A control method of an all-terrain armored vehicle independent cooling system is applied, the corresponding relation between the rotating speed of an axial flow fan and the current output to a two-position three-way electro-hydraulic control valve by a controller is determined according to the power characteristics of a hydraulic motor and the axial flow fan, and the corresponding relation between the rotating speed and the current is stored for calling; the controller monitors and diagnoses the temperature signals of the cooling media in real time, and outputs corresponding current values to the two-position three-way electro-hydraulic control valve, so that the dynamic adjustment of the rotating speed of the axial flow fan is realized.
Further, the temperature signals of the cooling medium comprise an inlet/outlet water temperature signal of the engine, an air-to-air cooling inlet/outlet temperature signal, a transmission oil inlet/outlet temperature signal, a transfer case inlet/outlet temperature signal and a hydraulic oil inlet/outlet temperature signal.
Further, when the working temperature of the cooling medium is lower than the designed optimal working temperature, the controller outputs the maximum current, and the axial flow fan operates at the lowest rotating speed; along with the continuous rise of the temperature of a medium in work, the output current of the controller is continuously reduced, the rotating speed of the fan is continuously increased, and the gradient of the change of the rotating speed and the temperature is k 1; when all cooling media are at the optimal working temperature, the change slope of the rotating speed-temperature is k 2; when the working temperature of any cooling medium is higher than the optimal working temperature, the change slope of the rotating speed-temperature is k 3; when the working temperature of any cooling medium is close to the alarm value, the axial flow fan works at the maximum rotating speed, so that the system is prevented from being overheated; the k1 is greater than the k3, the k3 is greater than the k 2.
The invention has the beneficial effects that:
this independent cooling system of full topography armoured vehicle utilizes closed cooling system to realize the independent heat dissipation of locomotive, has effectively solved prior art oil tank totality big partially, leads to the problem that whole car weight aggravates, and hydraulic tank and hydraulic oil use amount reduce by a wide margin, lays solid basis for the lightweight design of equipment, improves the loading capacity and the mobility of equipment. The axial flow fan is adopted to replace the traditional axial flow fan, so that the volume and the weight of the radiator are greatly reduced, and the lightweight design of the armored vehicle is guaranteed.
This independent cooling system of full topography armored car sets up two-way closed hydraulic pump device, and along with the constantly increasing of engine speed, the hydraulic pump discharge capacity can realize automatically regulated. The bidirectional closed hydraulic pump device comprises a two-position three-way electro-hydraulic control valve, and the coil current of the bidirectional closed hydraulic pump device has a unique corresponding relation with the working pressure of the system; according to the power characteristics of the hydraulic pump and the axial flow fan, the corresponding maximum rotating speed of the fan can be calculated according to the working pressure value of each system. Therefore, during actual control, the working pressure of the system can be determined by outputting one control current every time, and the maximum power and the rotating speed of the hydraulic motor and the fan under the working pressure of the system are limited. The bidirectional closed hydraulic pump device is provided with the swash plate direction control valve, after the radiating system works for a long time, the rotating direction of the fan can be changed, dust or other sundries on the radiator can be reversely blown, the radiating efficiency is ensured, and the bidirectional closed hydraulic pump device has the advantages of compact construction, simplicity in operation, convenience in maintenance and the like.
According to the control method of the independent cooling system of the all-terrain armored vehicle, the dynamic adjustment of the rotating speed of the axial flow fan can be realized only by determining the corresponding relation between the rotating speed of the axial flow fan and the control current and outputting the corresponding control current according to the monitored and diagnosed temperature signals of the cooling media, and the control process is extremely simple.
Drawings
FIG. 1 is a schematic structural view of an independent heat dissipation system of an all-terrain armored vehicle according to the present invention;
FIG. 2 is a schematic structural diagram of a bidirectional closed hydraulic pump device in an independent heat dissipation system of an all-terrain armored vehicle according to the present invention;
FIG. 3 is a schematic structural view of a quantitative hydraulic motor device in an independent heat dissipation system of an all-terrain armored vehicle according to the present invention;
FIG. 4 is a schematic diagram of a relationship curve between system pressure and control current of the independent cooling system of the all-terrain armored vehicle of the present invention;
FIG. 5 is a schematic diagram of a speed-power relationship derived from power characteristics of an axial fan and a hydraulic motor;
fig. 6 is a schematic diagram of a temperature-rotation speed correspondence relationship under each working condition in the control method of the independent heat dissipation system of the all-terrain armored vehicle.
Detailed Description
The technical solutions of the present invention are further described in detail below with reference to the accompanying drawings, but the scope of the present invention is not limited to the following.
As shown in fig. 1 to 3, an independent heat dissipation system for an all-terrain armored vehicle includes a power take-off device 100, a bidirectional closed hydraulic pump device 200, an oil tank 500, a fixed-displacement hydraulic motor device 600, and an axial flow fan 400.
As shown in fig. 2, the bidirectional closed hydraulic pump device 200 is an integrated device, and includes a closed pump 220, a swash plate direction control valve 210, a variable piston 230, a first throttle valve 240, a second throttle valve 250, a two-position three-way electro-hydraulic control valve 260, and a shuttle valve 270. Two working oil ports of the closed pump 220 are respectively provided with an oil port A and an oil port B in a communicated manner, an oil drainage port of the closed pump 220 is provided with an oil port T in a communicated manner, and the oil port T is communicated with the oil tank 500. The swash plate direction control valve 210 serves to change the pumping direction of the closed type pump 220. Variable piston 230 includes the cylinder, the piston, piston rod and spring, piston slidable set up in the cylinder, c chamber and d chamber are separated into with the cylinder to the piston, and spring and piston rod all set up in the c intracavity, and the both ends of spring are connected with piston and cylinder respectively, and the one end and the piston of piston rod are connected, and the other end of piston rod passes the cylinder and is connected with the sloping cam plate of closed pump 220, and it is used for adjusting the plunger sloping cam plate angle of closed pump 220, finally realizes the regulation of pump discharge capacity. The c chamber of the variable piston 230 communicates with the port T, and the d chamber of the variable piston 230 communicates with the port T through the second orifice 250. Two oil inlets of the shuttle valve 270 are respectively communicated with the oil port a and the oil port B, an oil outlet of the shuttle valve 270 is communicated with a pressure oil port of the two-position three-way electro-hydraulic control valve 260, and the shuttle valve 270 can extract high-pressure oil of the oil port a (or the oil port B) to control the two-position three-way electro-hydraulic control valve 260. The working port of the two-position three-way electro-hydraulic control valve 260 is communicated with the d-cavity of the variable piston 230 through the first throttle valve 240, and the oil return port of the two-position three-way electro-hydraulic control valve 260 is communicated with the port T. The output shaft of the power take-off 100 is in transmission connection with the power shaft of the closed pump 220, the power take-off can be selected from devices for transmitting torque, such as a gearbox, a transfer case and the like, and the input shaft of the power take-off is directly connected with the engine of the locomotive when the power take-off is used, so that the power of the engine of the locomotive is directly transmitted to the closed pump 220. The quantitative hydraulic motor device 600 includes a hydraulic motor 620, the hydraulic motor 620 includes a working oil port a1 and a working oil port B1, the oil port a and the oil port B of the closed pump 220 are respectively communicated with the working oil port a1 and the working oil port B1 of the hydraulic motor 620, an output shaft of the hydraulic motor 620 is connected with an input shaft of the axial flow fan 400, and an oil drain port of the hydraulic motor 620 is communicated with the oil tank 500.
The two-position three-way electro-hydraulic control valve 260 is an electro-hydraulic integrated control valve, and can maintain the dynamic balance relationship of the system pressure through the stress balance at the two ends of the valve core, and the stress relationship at the two ends of the valve core is as follows:
Pn×Sa1+Fa1+FAn= Fb1
namely: pn = (Fb 1-Fa 1-FAn)/Sa 1
In the formula:
the spring force at the end Fa1- - -a1 is constant in practical application according to the type of valve,
pn-the working pressure of the system,
the acting area of the hydraulic oil at the Sa1- - -a1 end is a fixed value in practical application according to the type of the valve,
the spring force at the end Fb1- - -b1 is constant in practical application according to the type of the valve,
FAn- -the magnetic force generated by the coil when the current signal An.
From the above formula, it can be seen that: when the current value An =0, that is, FAn =0, the operating pressure Pn of the system at this time = Pmax. Conversely, when current value An = Amax, that is, FAn = FAmax, operating pressure Pn of the system at this time = Pmin.
The above system pressure versus control current relationship is shown in fig. 4. As can be seen from the graph, the two-position three-way electro-hydraulic control valve is used in the graph, and when the current value is between (160-640) mA, the current value and the pressure value are in a nearly linear decreasing relation. From this, it can be found that the coil current An of the two-position three-way electrohydraulic control valve 260 has a unique correspondence relationship with the system operating pressure Pn.
Combining the power characteristics of the hydraulic motor 620 and the axial fan 400: under the condition that the pressure of the hydraulic system is determined, the output power of the hydraulic motor is in direct proportion to the rotating speed; the power of the fan is proportional to the cube of the speed. The torque must meet the requirement that Mma is not less than M wind, that is, the power Pma is not less than P wind at the same rotation speed, the hydraulic motor 620 can drive the axial flow fan 400 to rotate. As shown in fig. 5, when the system pressure Pn is a fixed value, and the rotation speed is between 0 and n, the closed pump 200 starts to operate at full displacement, the output power of the hydraulic motor is greater than the driving power of the fan, the motor can normally drive the fan to rotate, and the flow rate of the hydraulic pump determines the rotation speed of the hydraulic motor/fan. While the maximum rotation speed and the maximum power output (corresponding to the flow rate Qn) under the pressure Pn are realized at the point H in fig. 5, at this time, the system flow rate will increase continuously with the increase of the rotation speed of the power take-off device 100, but because the torque M is less than the torque M of the motor M of the fan, the rotation speed of the motor/fan will not increase or increase. At this time, the hydraulic oil flows to the first throttle valve 240 through the shuttle valve 270 and the two-position three-way electro-hydraulic control valve 260, enters the d cavity of the variable piston 230, pushes the swash plate of the closed pump 220, reduces the displacement of the swash plate, and finally achieves the dynamic adjustment process of the system flow Q = Qn. Therefore, the maximum rotating speed corresponding to the air outlet machine can be calculated for each system working pressure value Pn.
When the system is cooled, the closed pump 220 rotates in the forward direction, high-pressure oil is pumped out from the oil port a and enters the hydraulic motor 620 to drive the axial flow fan 400 to rotate so as to cool the system, and return oil of the hydraulic motor 620 returns to the closed pump 220 through the oil port B. By controlling the coil current An of the two-position three-way electro-hydraulic control valve 260, the unique system working pressure Pn can be controlled, so that the rotation speed of the axial flow fan 400 can be adjusted, and the heat dissipation requirements under different working conditions can be met. From this, utilize closed cooling system to realize the independent heat dissipation of locomotive, effectively solved among the prior art oil tank totality big partially, lead to the problem that whole car weight aggravates, hydraulic tank and hydraulic oil use amount reduce by a wide margin, lay solid basis for the lightweight design of equipment, improve the loading capacity and the mobility of equipment. Compared with the prior art, the axial flow fan 400 is adopted to replace the traditional axial flow fan, the efficiency is improved to more than 75% from the traditional 40-50%, the size and the weight of the radiator are greatly reduced, and the lightweight design of the armored vehicle is guaranteed.
The swash plate direction control valve 210 is provided to change the pumping direction of the closed type pump 220. After the heat dissipation system works for a long time, a large amount of dust or other impurities are attached to the heat radiator, so that the heat dissipation efficiency is seriously reduced. At this time, the swash plate direction control valve 210 is only required to be operated to reversely rotate the fan to blow out the impurities or dust, so that the radiator can be recovered to the optimal working state. The device has the advantages of compact construction, simple operation, convenient maintenance and the like.
Further, the independent cooling system of the all-terrain armored vehicle further comprises an oil supplementing device. The oil supplementing device is used for supplementing the hydraulic oil shortage caused by leakage of the flushing valve and the system, and comprises an oil supplementing pump 510, a first check valve 310, a second check valve 320 and an oil supplementing overflow valve 330. The power shaft of the oil replenishing pump 510 is in transmission connection with the power shaft of the closed pump 220, the oil suction port of the oil replenishing pump 510 is communicated with the oil tank 500, the pump oil port of the oil replenishing pump 510 is communicated with the oil inlet of the first check valve 310, the oil inlet of the second check valve 320 and the oil inlet of the oil replenishing overflow valve 330, the oil outlet of the first check valve 310 is communicated with the oil port A, the oil outlet of the second check valve 320 is communicated with the oil port B, and the overflow port of the oil replenishing overflow valve 330 is communicated with the oil tank 500. When the locomotive runs, the power takeoff device 100 drives the oil supplementing pump 510 to rotate, hydraulic oil in the oil tank 500 is pumped to the oil inlet of the first check valve 310, the oil inlet of the second check valve 320 and the oil inlet of the oil supplementing overflow valve 330, and when hydraulic oil needs to be supplemented to the system, the pressure oil can directly open the valve core of the first check valve 310 (or the second check valve 320) to supplement the oil to the system; when the system does not need oil supplement, the oil supplement overflow valve 330 is opened and directly flows back to the oil tank 500, so that the flow balance of the system is kept. Further, an oil suction filter 520 is arranged between the oil replenishing pump 510 and the oil tank 500, so that the hydraulic oil entering the system is ensured to be clean.
In practice, the constant displacement hydraulic motor assembly 600 is an integrated unit that further includes a flush valve 610. The flushing valve 610 comprises a three-position three-way electromagnetic valve and a flushing overflow valve, wherein an O port and a P port of the three-position three-way electromagnetic valve are respectively communicated with an oil port A and an oil port B, the A port of the three-position three-way electromagnetic valve is communicated with an oil inlet of the flushing overflow valve, and an overflow port of the flushing overflow valve is communicated with an oil drainage port of a hydraulic motor. The oil drain of the closed system can be realized by controlling the communication between the port O and the port A (or the communication between the port P and the port A) of the three-position three-way electromagnetic valve. In particular, a cooler 530 is also provided. The oil drain port of the hydraulic motor 620, the overflow port and the oil port T of the oil-supplementing overflow valve 330 are communicated with the oil tank 500 through the cooler 530, and the hydraulic oil flowing back to the oil tank 500 in the closed system is cooled by the cooler 530, so that heat can be effectively released, and the problem of heat dissipation of the closed system is solved.
When the independent cooling system of the all-terrain armored vehicle is used, the controller 600 is further arranged, and the controller 600 is respectively electrically connected with the swash plate direction control valve 210 and the two-position three-way electro-hydraulic control valve 260.
The control method comprises the following steps:
according to the power characteristics of the hydraulic motor 620 and the axial flow fan 400, the corresponding relation between the rotating speed of the axial flow fan 400 and the current output to the two-position three-way electro-hydraulic control valve 260 by the controller 600 is determined, and the corresponding relation between the rotating speed and the current is stored for calling. As can be seen from the foregoing, the maximum power/rotation speed of the axial flow fan 400 and the output current of the controller are in a unique corresponding relationship, which can be obtained by calculation, or by measuring the actual rotation speed of the fan under different control currents.
The controller 600 monitors and diagnoses temperature signals of the cooling media in real time, outputs corresponding current values to the two-position three-way electro-hydraulic control valve 260, achieves dynamic adjustment of the rotating speed of the axial flow fan 400, achieves heat dissipation of the locomotive as required, and improves energy-saving and emission-reducing effects of the vehicle. The controller 600 also monitors the state of the swash plate direction control valve 210 in real time, and when a large amount of dust or other impurities attached to the radiator need to be cleaned, the swash plate direction control valve 210 is controlled to change the direction of the swash plate, so that the axial flow fan 400 is reversed, and the use requirements of different working conditions are met.
The temperature signals of the cooling medium comprise an inlet/outlet water temperature signal of the engine, an air-to-air cooling inlet/outlet temperature signal, a transmission oil inlet/outlet temperature signal, a transfer case inlet/outlet temperature signal and a hydraulic oil inlet/outlet temperature signal.
In specific implementation, the required fan power of the cooling system can be calculated by combining the required cooling power of the cooling system at different medium temperatures, and the required input current value at different temperatures is confirmed.
In different heat dissipation stages, the change slopes of the rotating speed and the temperature are respectively k1, k2 and k3, wherein k1 is larger than k3, and k3 is larger than k 2. As shown in fig. 6, when the operating temperatures of the cooling mediums are all lower than the designed optimal operating temperature, the controller 600 outputs the maximum current, and the axial flow fan 400 operates at the lowest rotational speed; with the continuous increase of the temperature of the medium in the working process, the output current of the controller 600 is continuously reduced, the rotating speed of the fan is continuously increased, and the gradient of the change of the rotating speed and the temperature is k 1; when all cooling media are at the optimal working temperature, the change slope of the rotating speed-temperature is k 2; when the working temperature of any cooling medium is higher than the optimal working temperature, the change slope of the rotating speed-temperature is k 3; when the working temperature of any cooling medium approaches the alarm value, the axial flow fan 400 works at the maximum rotating speed, so that the system is prevented from being overheated; when the cooling medium temperature is reduced to the optimal working temperature, the change slope of the rotating speed and the temperature is executed according to k2, and the system is ensured to be operated during the optimal working temperature.
The foregoing is illustrative of the preferred embodiments of this invention, and it is to be understood that the invention is not limited to the precise form disclosed herein and that various other combinations, modifications, and environments may be resorted to, falling within the scope of the concept as disclosed herein, either as described above or as apparent to those skilled in the relevant art. And that modifications and variations may be effected by those skilled in the art without departing from the spirit and scope of the invention as defined by the appended claims.
Claims (9)
1. An independent heat dissipation system of an all-terrain armored vehicle is characterized by comprising a power take-off device (100), a bidirectional closed hydraulic pump device (200), an oil tank (500), a quantitative hydraulic motor device (600) and an axial flow fan (400);
the bidirectional closed hydraulic pump device (200) comprises a closed pump (220), a swash plate direction control valve (210), a variable piston (230), a first throttle valve (240), a second throttle valve (250), a two-position three-way electro-hydraulic control valve (260) and a shuttle valve (270),
two working oil ports of the closed pump (220) are respectively provided with an oil port A and an oil port B in a communicated manner, an oil drainage port of the closed pump (220) is provided with an oil port T in a communicated manner, the oil port T is communicated with the oil tank (500), the swash plate direction control valve (210) is used for changing the oil pumping direction of the closed pump (220), the variable piston (230) is used for adjusting the displacement of the closed pump (220),
the variable piston (230) comprises a cylinder barrel, a piston rod and a spring, the piston is slidably arranged in the cylinder barrel, the cylinder barrel is divided into a c cavity and a d cavity by the piston, the spring and the piston rod are both arranged in the c cavity, two ends of the spring are respectively connected with the piston and the cylinder barrel, one end of the piston rod is connected with the piston, the other end of the piston rod penetrates through the cylinder barrel and is connected with a swash plate of the closed pump (220), the c cavity is communicated with the oil port T, and the d cavity is communicated with the oil port T through the second throttle valve (250),
two oil inlets of the shuttle valve (270) are respectively communicated with the oil port A and the oil port B, an oil outlet of the shuttle valve (270) is communicated with a pressure oil port of the two-position three-way electro-hydraulic control valve (260), a working oil port of the two-position three-way electro-hydraulic control valve (260) is communicated with the cavity d through the first throttling valve (240), and an oil return port of the two-position three-way electro-hydraulic control valve (260) is communicated with the oil port T;
the output shaft of the power taking device (100) is in transmission connection with the power shaft of the closed pump (220), the quantitative hydraulic motor device (600) comprises a hydraulic motor (620), the hydraulic motor (620) comprises a working oil port A1 and a working oil port B1, the oil port A and the oil port B are respectively communicated with a working oil port A1 and a working oil port B1 of the hydraulic motor (620), the output shaft of the hydraulic motor (620) is connected with the input shaft of the axial flow fan (400), and the oil drainage port of the hydraulic motor (620) is communicated with the oil tank (500).
2. The independent heat dissipation system of the all-terrain armored vehicle of claim 1, further comprising an oil replenishment device, the oil supplementing device comprises an oil supplementing pump (510), a first check valve (310), a second check valve (320) and an oil supplementing overflow valve (330), the power shaft of the oil replenishing pump (510) is in transmission connection with the power shaft of the closed pump (220), an oil suction port of the oil replenishing pump (510) is communicated with the oil tank (500), a pump oil port of the oil replenishing pump (510) is communicated with an oil inlet of the first check valve (310), an oil inlet of the second check valve (320) and an oil inlet of the oil replenishing overflow valve (330), an oil outlet of the first check valve (310) is communicated with the oil port A, an oil outlet of the second check valve (320) is communicated with the oil port B, and an overflow port of the oil supplementing overflow valve (330) is communicated with the oil tank (500).
3. The independent cooling system of the all-terrain armored vehicle as claimed in claim 2, wherein an oil suction filter (520) is arranged between the oil supply pump (510) and the oil tank (500).
4. The independent cooling system of the all-terrain armored vehicle according to claim 3, wherein the quantitative hydraulic motor device (600) further comprises a flushing valve (610), the flushing valve (610) comprises a three-position three-way solenoid valve and a flushing overflow valve, an O port and a P port of the three-position three-way solenoid valve are respectively communicated with the oil port A and the oil port B, an A port of the three-position three-way solenoid valve is communicated with an oil inlet of the flushing overflow valve, and an overflow port of the flushing overflow valve is communicated with an oil drainage port of the hydraulic motor.
5. The independent cooling system of the all-terrain armored vehicle as claimed in claim 4, further comprising a cooler (530), wherein the oil drain port of the hydraulic motor (620), the overflow port of the oil-replenishing overflow valve (330) and the oil port T are all communicated with the oil tank (500) through the cooler (530).
6. The all-terrain armored vehicle independent cooling system of claim 5, further comprising a controller (600), the controller (600) being in electrical communication with the swashplate directional control valve (210) and the two-position, three-way, electrically-energized, hydraulic control valve (260), respectively.
7. The control method of the independent cooling system of the all-terrain armored vehicle according to claim 6, wherein the corresponding relationship between the rotating speed of the axial flow fan (400) and the current output by the controller (600) to the two-position three-way electro-hydraulic control valve (260) is determined according to the power characteristics of the hydraulic motor (620) and the axial flow fan (400), and the corresponding relationship between the rotating speed and the current is stored for later use; the controller (600) monitors and diagnoses the temperature signals of the cooling media in real time, outputs corresponding current values to the two-position three-way electro-hydraulic control valve (260), and achieves dynamic adjustment of the rotating speed of the axial flow fan (400).
8. The method of claim 7, wherein the temperature signals of the cooling medium include an engine inlet/outlet water temperature signal, an air-to-air cooling inlet/outlet temperature signal, a transmission oil inlet/outlet temperature signal, a transfer case inlet/outlet temperature signal, and a hydraulic oil inlet/outlet temperature signal.
9. The control method of the independent cooling system of the all-terrain armored vehicle as claimed in claim 8, wherein when the working temperatures of the cooling mediums are all lower than the designed optimal working temperature, the controller (600) outputs the maximum current, and the axial flow fan (400) operates at the lowest rotation speed; along with the continuous rise of the temperature of a medium in work, the output current of the controller (600) is continuously reduced, the rotating speed of the fan is continuously increased, and the gradient of the change of the rotating speed and the temperature is k 1; when all cooling media are at the optimal working temperature, the change slope of the rotating speed-temperature is k 2; when the working temperature of any cooling medium is higher than the optimal working temperature, the change slope of the rotating speed-temperature is k 3; when the working temperature of any cooling medium is close to the alarm value, the axial flow fan (400) works at the maximum rotating speed, so that the system is prevented from being overheated; the k1 is greater than the k3, the k3 is greater than the k 2.
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