Heat sink for regenerative hydraulic system and heat sink method

Abstract

The present application relates to the technical field of hydraulic equipment, and particularly relates to a heat storage type hydraulic system heat dissipation device and a heat dissipation method. The heat dissipation device comprises a hydraulic oil storage tank, a cooling liquid circulating pipeline, a partition wall type heat exchanger, a circulating pump, an air-cooled radiator, a preheating heat accumulator and an intelligent monitoring assembly. The intelligent monitoring assembly monitors the temperature of the hydraulic system, and judges the preheating state, the back heat charging state, the normal working state or the over-temperature state of the hydraulic system, so as to control the heat dissipation device to operate in the air-cooled main circulating mode or the preheating bypass circulating mode according to the state. The present application can store the waste heat of the hydraulic system during high-temperature working, is used for preheating the oil, and can smooth the temperature fluctuation of the hydraulic oil and improve the air-side heat transfer coefficient through the temperature equalizing heat storage block arranged on the outer surface of the heat dissipation fin, so as to simultaneously improve the preheating and heat dissipation efficiency, reduce the energy consumption, prolong the shutdown cycle and the service life of the hydraulic system.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of hydraulic equipment, in particular to a heat accumulation type hydraulic system heat dissipation device and heat dissipation method. BACKGROUND

[0002] Large engineering machinery such as excavators and rotary drilling rigs need to work for a long time, and the hydraulic system generates a large amount of heat that needs to be dissipated in time. The existing hydraulic system hydraulic oil heat dissipation working principle is: the hydraulic oil in the hydraulic oil tank is pumped out by the oil pump and enters the radiator, and the high-temperature hydraulic oil and cold medium such as cold air in the radiator are exchanged to reduce the temperature of the hydraulic oil. The hydraulic oil with reduced temperature flows back to the hydraulic oil tank for the main pump to suck oil, and the cycle realizes the cooling of the hydraulic oil in the hydraulic system.

[0003] In summer, the high ambient temperature often causes the hydraulic components of the engineering machinery to overheat, which must be shut down for maintenance to avoid failure. At the same time, the hydraulic components of the engineering machinery are severely damaged in high-temperature environments, which seriously affects the service life of the machinery. In winter or cold highland areas, the engineering machinery needs to be preheated for a long time before it can work normally, which seriously wastes time and energy.

[0004] In summary, there is currently a lack of hydraulic system heat dissipation devices and heat dissipation methods that take into account efficient preheating and efficient heat dissipation. SUMMARY

[0005] The purpose of the present application is to provide a heat accumulation type hydraulic system heat dissipation device and heat dissipation method to solve the technical problem that the current hydraulic system heat dissipation device and heat dissipation method cannot simultaneously realize efficient preheating and efficient heat dissipation.

[0006] In order to solve the above technical problems, the application provides a heat storage type hydraulic system heat dissipation device, which comprises: a hydraulic oil storage tank provided with an upper oil return port and a lower oil outlet port; a cooling liquid circulation pipeline comprising a hydraulic oil heat exchange pipe section, an air-cooled heat dissipation pipe section, a preheating pipe section, a first three-way valve and a second three-way valve; the upper end of the hydraulic oil heat exchange pipe section, the upper end of the air-cooled heat dissipation pipe section and the upper end of the preheating pipe section are connected to the three interfaces of the first three-way valve, respectively; the lower end of the hydraulic oil heat exchange pipe section, the lower end of the air-cooled heat dissipation pipe section and the lower end of the preheating pipe section are connected to the three interfaces of the second three-way valve, respectively; a partition wall type heat exchanger and a circulating pump connected in series are arranged on the hydraulic oil heat exchange pipe section, the partition wall type heat exchanger is vertically arranged in the hydraulic oil storage tank, the cooling liquid outlet of the partition wall type heat exchanger is at the upper end and the inlet is at the lower end; the circulating pump is used to maintain the cooling liquid in the partition wall type heat exchanger to flow from the lower end to the upper end; an air-cooled radiator is arranged on the air-cooled heat dissipation pipe section, the air-cooled radiator comprises an upper header, a lower header, a plurality of parallel arranged heat dissipation fins and a heat dissipation fan; the inside of the heat dissipation fin is provided with vertically connected cooling liquid pipelines, the upper end of the cooling liquid pipeline is connected to the upper header, and the lower end of the cooling liquid pipeline is connected to the lower header; the surface of the heat dissipation fin is provided with an array of temperature equalizing heat storage blocks, the temperature equalizing heat storage block comprises a first phase change heat storage working medium, the phase change temperature of the first phase change heat storage working medium is a first phase change temperature, and the first phase change temperature is lower than the upper limit of the working temperature of the cooling liquid; the air outlet direction of the heat dissipation fan is vertically upward and parallel to the heat dissipation fin; a preheating heat accumulator is arranged on the preheating pipe section, the preheating heat accumulator comprises a second phase change heat storage working medium, the phase change temperature of the second phase change heat storage working medium is a second phase change temperature, and the second phase change temperature is higher than the lower limit of the working temperature of the cooling liquid; an intelligent monitoring assembly is provided with the phase change temperature of the working medium of the preheating heat accumulator, the lower limit and the upper limit of the working temperature of the cooling liquid, is used to obtain the outlet temperature of the partition wall type heat exchanger and the working medium temperature of the preheating heat accumulator, controls the first three-way valve and the second three-way valve to make the cooling liquid circulation pipeline operate in a specific circulation mode; the specific circulation mode comprises an air-cooled main circulation mode and a preheating bypass circulation mode; in the air-cooled main circulation mode, the hydraulic oil heat exchange pipe section is connected to the air-cooled heat dissipation pipe section and disconnected from the preheating pipe section; in the preheating bypass circulation mode, the hydraulic oil heat exchange pipe section is connected to the preheating pipe section and disconnected from the air-cooled heat dissipation pipe section; if the outlet temperature of the partition wall type heat exchanger is lower than the lower limit of the working temperature of the cooling liquid, the preheating bypass circulation mode is adjusted; if the outlet temperature of the partition wall type heat exchanger is not lower than the lower limit of the working temperature of the cooling liquid and not higher than the phase change temperature of the working medium of the preheating heat accumulator, the air-cooled main circulation mode is adjusted; if the outlet temperature of the partition wall type heat exchanger is higher than the phase change temperature of the working medium of the preheating heat accumulator and the working medium temperature of the preheating heat accumulator is lower than the phase change temperature of the working medium thereof, the preheating bypass circulation mode is adjusted.If the outlet temperature of the partition wall heat exchanger is higher than the phase transition temperature of the working medium of the preheating regenerator, and the working medium temperature of the preheating regenerator is not lower than the phase transition temperature of the working medium, the preheating bypass circulation mode is adjusted to; the intelligent monitoring component is also used for controlling the power of the circulating pump and the cooling fan; if the outlet temperature of the partition wall heat exchanger is higher than the upper limit of the working temperature of the cooling liquid, the circulating pump and the cooling fan are controlled to be opened in large power.

[0007] Further, the phase transition heat storage amount of the preheating regenerator is greater than the heat required for heating all the hydraulic oil from the local minimum temperature to the lower limit of the working temperature of the cooling liquid.

[0008] Further, the preheating regenerator comprises a plurality of detachable heat storage components.

[0009] Further, the preheating pipe section is further provided with a preheating heater; if the working medium temperature of the preheating regenerator is lower than the lower limit of the working temperature of the cooling liquid, the intelligent monitoring component controls the preheating heater to be opened.

[0010] Further, the cooling fan is installed directly above the cooling fins, and the cooling fan and the upper part of the cooling fins are provided with an enclosed air duct, and the lower part of the cooling fins is provided with a flow guide vane.

[0011] Further, the uniform temperature heat storage blocks are arranged in series or staggered.

[0012] The application also provides a heat dissipation method of a regenerative hydraulic system, which is used for the heat dissipation device of the regenerative hydraulic system and comprises the following steps: obtaining the phase transition temperature of the working medium of the preheating regenerator, the lower limit and the upper limit of the working temperature of the cooling liquid; obtaining the outlet temperature of the partition wall heat exchanger and the working medium temperature of the preheating regenerator; judging the state of the hydraulic system, wherein the state of the hydraulic system comprises a preheating state, a reverse heat charging state, a normal working state and an over-temperature state; and controlling the circulation mode of the cooling liquid circulation pipeline and the power of the circulating pump and the cooling fan according to the state of the hydraulic system.

[0013] If the preheating state is reached, the preheating bypass circulation mode is adjusted to; the judgment condition of the preheating state is that the outlet temperature of the partition wall heat exchanger is lower than the lower limit of the working temperature of the cooling liquid; if the normal working state is reached, the air-cooled main circulation mode is adjusted to; the judgment condition of the normal working state is that the outlet temperature of the partition wall heat exchanger is not lower than the lower limit of the working temperature of the cooling liquid and not higher than the phase transition temperature of the working medium of the preheating regenerator; if the over-temperature state is reached, the power of the circulating pump and the cooling fan is increased; and the judgment condition of the over-temperature state is that the outlet temperature of the partition wall heat exchanger is higher than the upper limit of the working temperature of the cooling liquid.

[0014] If in the anti-heat charging state, adjust to the preheating bypass circulation mode; the judgment condition of the anti-heat charging state: the outlet temperature of the partition wall heat exchanger is higher than the phase change temperature of the working medium of the preheating accumulator, and the working medium temperature of the preheating accumulator is lower than the phase change temperature of the working medium thereof.

[0015] Further, the state of the hydraulic system further includes a preheating insufficient state; if in the preheating insufficient state, adjust to the preheating bypass circulation mode, and turn on the preheating heater.

[0016] The beneficial effects of the present application are that the excess heat during high-temperature operation of the hydraulic system is stored in the preheating accumulator, which can cool the auxiliary cooling hydraulic oil on one hand, and reduce the preheating time and energy consumption on the other hand; the working medium flow directions of the partition wall heat exchanger and the air-cooled radiator are both arranged in a counter-flow manner, which can improve the heat transfer coefficient; the cooling liquid in the partition wall heat exchanger flows upward due to the increase of temperature and the decrease of density, and the cooling liquid in the air-cooled radiator flows downward due to the decrease of temperature and the increase of density, forming a natural circulation, which can reduce the power consumption of the circulating pump; the intelligent monitoring assembly can autonomously determine the state of the hydraulic system and control the pipeline circulation mode and the equipment operation state through the monitored temperature data, which is safe and efficient; the temperature equalization storage blocks arranged on the surface of the radiating fins can suppress temperature fluctuations and reduce thermal stress, thereby prolonging the shutdown cycle and service life of the hydraulic system; the arrayed temperature equalization storage blocks can also increase the turbulence intensity and destroy the laminar boundary layer, thereby increasing the convective heat transfer coefficient of the outer layer of the radiating fins. BRIEF DESCRIPTION OF DRAWINGS

[0017] The accompanying drawings, which form a part of this application, are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification. The illustrations are shown to explain the present application and are not intended to limit the present application in an inappropriate manner. In the drawings:

[0018] Figure 1 FIG. 1 is a structural schematic view of a heat storage type hydraulic system heat dissipation device according to an embodiment of the present application;

[0019] Figure 2 FIG. 2 is a sectional view of the heat storage type hydraulic system heat dissipation device according to the embodiment of the present application; Figure 1

[0020] Figure 3 FIG. 3 is a detailed structural schematic view of a radiating fin according to the embodiment of the present application;

[0021] Figure 4 FIG. 4 is a flow chart of a heat dissipation method of a heat storage type hydraulic system according to the embodiment of the present application;

[0022] In the drawings:

[0023] 1 - hydraulic oil storage tank, 11 - upper oil return port, 12 - lower oil outlet port,

[0024] ​2-cooling liquid circulation pipeline, 21-liquid oil heat exchange pipe section, 22-air cooling radiator pipe section, 23-preheating pipe section, 24-first three-way valve, 25-second three-way valve,

[0025] 3-interwall heat exchanger,

[0026] 4-circulating pump,

[0027] 5-air cooling radiator, 51-upper header, 52-lower header, 53-radiator fin, 531-cooling liquid pipeline, 532-temperature equalizing heat storage block, 54-radiator fan,

[0028] 6-preheating heat accumulator. DETAILED DESCRIPTION

[0029] In order to make the purpose, technical scheme and advantages of the embodiments of the present application more clear, the technical scheme of the present application will be described clearly and completely below in conjunction with the drawings. Obviously, the described embodiments are some of the embodiments of the present application, but not all the embodiments. Based on the embodiments in the present application, all other embodiments of those skilled in the art without creative labor are within the protection scope of the present application.

[0030] Embodiment one

[0031] In the present embodiment, a heat dissipation device for a heat storage type hydraulic system is provided, a structural schematic diagram of which is shown in Figure 1 and Figure 2 , comprising: a hydraulic oil storage tank 1, a cooling liquid circulation pipeline 2, an interwall heat exchanger 3, a circulating pump 4, an air cooling radiator 5, and a preheating heat accumulator 6.

[0032] The hydraulic oil storage tank 1 is provided with an upper oil return port 11 and a lower oil outlet 12. When the hydraulic system is running, hydraulic oil flows out from the lower oil outlet 12 and flows into from the upper oil return port 11.

[0033] The cooling liquid circulation pipeline 2 comprises a liquid oil heat exchange pipe section 21, an air cooling radiator pipe section 22, a preheating pipe section 23, a first three-way valve 24, and a second three-way valve 25. The upper end of the liquid oil heat exchange pipe section 21, the upper end of the air cooling radiator pipe section 22, and the upper end of the preheating pipe section 23 are respectively connected to the three interfaces of the first three-way valve 24. The lower end of the liquid oil heat exchange pipe section 21, the lower end of the air cooling radiator pipe section 22, and the lower end of the preheating pipe section 23 are respectively connected to the three interfaces of the second three-way valve 25. The first three-way valve 24 and the second three-way valve 25 divide the entire cooling liquid circulation pipeline 2 into three sections, and by changing the gears of the first three-way valve 24 and the second three-way valve 25, different circulation loops can be selectively formed.

[0034] A partition wall heat exchanger 3 and a circulating pump 4 are connected in series on the hydraulic oil heat exchange tube section 21. The partition wall heat exchanger 3 is vertically arranged inside the hydraulic oil storage tank 1, with the coolant outlet at the top and the inlet at the bottom. The circulating pump 4 is used to maintain the coolant flow from bottom to top within the partition wall heat exchanger 3. Inside the hydraulic oil storage tank 1, the fluid on the outside of the partition wall heat exchanger 3 is hydraulic oil, and the fluid on the inside is coolant. The two fluids exchange heat through the partition wall, with the hydraulic oil flowing downwards and the coolant flowing upwards. This counter-current arrangement maximizes the heat transfer coefficient. Simultaneously, the coolant's temperature rises and density decreases after absorption, naturally creating upward buoyancy, which reduces the power consumption of the circulating pump 4. The partition wall heat exchanger 3 can be a plate heat exchanger, a coil heat exchanger, a shell-and-tube heat exchanger, etc.

[0035] The air-cooled heat sink 5 is mounted on the air-cooled heat pipe section 22. The air-cooled heat sink 5 includes an upper manifold 51, a lower manifold 52, several parallel heat sinks 53, and a cooling fan 54; for example... Figure 3 As shown, the heat sink 53 has vertically parallel coolant pipes 531 inside. The upper ends of the coolant pipes 531 are all connected to the upper manifold 51, and the lower ends of the coolant pipes are all connected to the lower manifold 52. The surface of the heat sink 53 is provided with an array of uniform temperature heat storage blocks 532. The uniform temperature heat storage blocks 532 contain a first phase change heat storage medium. The phase change temperature is the first phase change temperature, which is lower than the upper limit of the coolant working temperature. The exhaust direction of the cooling fan 54 is vertically upward and parallel to the heat sink 53. The air-cooled radiator 5 uses the cold air outside to lower the temperature of the coolant inside. The parallel arrangement of several heat sinks 5 can increase the heat exchange area. The coolant inside the air-cooled radiator 5 decreases in temperature and increases in density, flowing downwards naturally. This, combined with the coolant in the aforementioned partition heat exchanger 3 which absorbs the coolant, increases in temperature and decreases in density, flowing upwards naturally, forms a natural circulation, which can reduce the power consumption of the circulation pump. The cold air outside the air-cooled radiator 5 is heated, decreases in density, and flows upwards naturally, consistent with the vertical upward air outlet direction of the cooling fan 54. This combination not only increases the airflow speed but also delivers hot air to higher levels, preventing hot air from accumulating near the outlet and thus preventing the intake air temperature from rising. The heat-equalizing blocks 532 disposed on the surface of the heat sink 53 can suppress temperature fluctuations. When the temperature of the hydraulic oil becomes excessively high in a short period due to increased output or deteriorated heat dissipation, the heat-equalizing blocks 532 can absorb this excess heat. When the temperature of the hydraulic oil drops in a short period, the heat-equalizing blocks 532 can release heat. A stable coolant temperature can ensure stable hydraulic oil temperature and stable heat dissipation of the air-cooled radiator 5, and can also reduce thermal stress, thereby extending the downtime and life of the hydraulic system. The arrayed heat-equalizing blocks 532 protrude from the surface of the heat sink 5, forming a turbulence-inducing element, which can increase the turbulence intensity and disrupt the laminar boundary layer, thereby increasing the convective heat transfer coefficient of the outer layer of the heat sink 5.

[0036] The preheating accumulator 6 is installed on the preheating pipe section 23. The preheating accumulator 6 contains a second phase change heat storage medium, the phase change temperature of which is higher than the lower limit of the coolant's operating temperature. The preheating accumulator 6 is used to absorb and store excess heat during the high-temperature operation of the hydraulic system. On the one hand, it can assist in cooling the hydraulic oil; on the other hand, it can release heat during the preheating stage of the hydraulic system, reducing preheating time and energy consumption.

[0037] The intelligent monitoring component is preset with the working fluid phase change temperature of the preheating accumulator 6 and the lower and upper limits of the coolant operating temperature. It is used to acquire the outlet temperature of the indirect heat exchanger 3 and the working fluid temperature of the preheating accumulator 6, and to control the first three-way valve 24 and the second three-way valve 25 to operate the coolant circulation pipeline 2 in a specific circulation mode. The specific circulation modes include an air-cooled main circulation mode and a preheating bypass circulation mode. In the air-cooled main circulation mode, the hydraulic oil heat exchange section 21 is connected to the air-cooled heat dissipation section 22 and disconnected from the preheating section 23. In the preheating bypass circulation mode, the hydraulic oil heat exchange section 21 is connected to the preheating section 23 and disconnected from the air-cooled heat dissipation section 22. The intelligent monitoring component monitors the operating status of the hydraulic system in real time and adjusts the circulation mode of the coolant circulation pipeline 2 according to the operating status.

[0038] If the outlet temperature of the indirect heat exchanger 3 is lower than the lower limit of the coolant's operating temperature, switch to preheating bypass circulation mode. During the initial startup of the hydraulic system, the hydraulic oil temperature is lower than the lower limit of the hydraulic oil's operating temperature, resulting in the outlet temperature of the indirect heat exchanger 3 also being lower than the lower limit of the coolant's operating temperature. At this time, preheating of the hydraulic oil is required. Therefore, the hydraulic oil heat exchange pipe section 21 and the preheating pipe section 23 are connected. The coolant circulates between the indirect heat exchanger 3 and the preheating accumulator 6. The preheating accumulator 6 releases heat to heat the coolant, which then heats the hydraulic oil in the hydraulic oil storage tank 1 through the indirect heat exchanger 3, thus completing the preheating of the hydraulic oil.

[0039] If the outlet temperature of the indirect heat exchanger 3 is not lower than the lower limit of the coolant's operating temperature and not higher than the working fluid phase change temperature of the preheating accumulator 6, the system is switched to air-cooled main circulation mode. As preheating completes, the hydraulic system begins to operate, and its temperature continues to rise. Therefore, the hydraulic oil heat exchange pipe section 21 and the air-cooled heat dissipation pipe section 22 are connected. At this time, the coolant circulates between the indirect heat exchanger 3 and the air-cooled radiator 5. The coolant releases heat through the indirect heat exchanger 3 to the coolant, and then releases heat through the air-cooled radiator 5 to the outer cold air, thus completing the cooling of the hydraulic oil.

[0040] If the outlet temperature of the indirect heat exchanger 3 is higher than the working fluid phase change temperature of the preheating accumulator 6, and the working fluid temperature of the preheating accumulator 6 is lower than its working fluid phase change temperature, the system is switched to preheating bypass circulation mode. If the hydraulic system operates at high power for a long time, its temperature will rise further, even exceeding the working fluid phase change temperature of the preheating accumulator 6. In this case, heat can be supplied to the preheating accumulator 6 in reverse. Therefore, the hydraulic oil heat exchange pipe section 21 and the preheating pipe section 23 are connected to complete the charging of the preheating accumulator 6, preparing it for the next hydraulic oil preheating.

[0041] If the outlet temperature of the indirect heat exchanger 3 is higher than the working fluid phase change temperature of the preheating accumulator 6, and the working fluid temperature of the preheating accumulator 6 is not lower than its working fluid phase change temperature, the system is switched to air-cooled main circulation mode. After the preheating accumulator 6 is fully charged, the hydraulic oil heat exchange pipe section 21 and the air-cooled heat dissipation pipe section 22 are still connected to continue hydraulic oil heat dissipation.

[0042] The intelligent monitoring component is also used to control the power of the circulating pump 4 and the cooling fan 54; if the outlet temperature of the indirect heat exchanger 3 is higher than the upper limit of the coolant's operating temperature, the circulating pump 4 and the cooling fan 54 will be operated at increased power. If the temperature of the hydraulic oil continues to rise, even exceeding its upper limit of operating temperature, resulting in the outlet temperature of the indirect heat exchanger 3 being higher than the upper limit of the coolant's operating temperature, this indicates insufficient heat dissipation power, so the power of the circulating pump 4 and the cooling fan 54 will be increased.

[0043] Furthermore, in order to prevent insufficient heat storage in the preheating accumulator 6, the phase change heat storage capacity of the preheating accumulator 6 can be increased, for example, it can be greater than the heat required for all hydraulic oils to rise from the local minimum temperature to the lower limit of the cooling oil operating temperature. In this way, even in the event of extreme low temperatures, the preheating accumulator 6 can meet the preheating requirements.

[0044] Preferably, in order to avoid having to carry an excessive amount of preheating accumulator 6 each time, the preheating accumulator 6 can be disassembled into several detachable heat storage components, so that the stored heat of the preheating accumulator 6 can be flexibly adjusted according to the ambient temperature or the work location.

[0045] Furthermore, to cope with emergencies such as extreme low temperatures or insufficient heating of the preheating accumulator 6, a preheating heater is also installed on the preheating pipe section 23; if the working fluid temperature of the preheating accumulator 6 is lower than the lower limit of the working temperature of the coolant, the intelligent monitoring component controls the preheating heater to be turned on, and the preheating heater serves as a backup preheating heat source.

[0046] Furthermore, the cooling fan 54 can be installed in various ways. It can be installed below the heat sink 53 at the air inlet as a blower, or above the heat sink 53 at the air outlet as an exhaust fan, or it can be installed both above and below.

[0047] Preferably, balancing structural simplicity and outstanding performance, the cooling fan 54 is mounted directly above the heat sink 53, and an enclosed air duct is provided around the upper part of the cooling fan 54 and the heat sink 53, while guide vanes are provided around the lower part of the heat sink 53. The cooling fan 54, mounted above the heat sink 53, acts as an exhaust fan at the air outlet, enhancing airflow and allowing hot air to be exhausted to a higher altitude, thus preventing hot air accumulation and increased intake temperature. The enclosed air duct and guide vanes guide gas flow, reducing air leakage and intake resistance.

[0048] Furthermore, the heat storage blocks 532 can be arranged in either a linear or staggered configuration. The heat storage blocks 532 act as a turbulence generator; a linear arrangement can reduce resistance and is suitable for structures with high inlet resistance, while a staggered arrangement can increase turbulence and is suitable for structures with high air-side thermal resistance. Therefore, the choice can be made according to specific needs.

[0049] Example 2

[0050] This embodiment provides a heat dissipation method for a heat storage hydraulic system, the process of which is as follows: Figure 4 As shown, it includes the following steps:

[0051] S101. Obtain the working fluid phase change temperature, coolant operating temperature lower limit and upper limit of the preheating accumulator 6;

[0052] S102. Obtain the outlet temperature of the indirect heat exchanger 3 and the working fluid temperature of the preheating accumulator 6.

[0053] S103. Determine the state of the hydraulic system. The state of the hydraulic system includes preheating state, reverse charging state, normal working state, and over-temperature state.

[0054] S104. Control the circulation mode of the coolant circulation pipeline 2, the power of the circulation pump 4 and the cooling fan 54 according to the state of the hydraulic system.

[0055] If it is in the preheating state, switch to the preheating bypass circulation mode; the condition for judging the preheating state is: the outlet temperature of the indirect heat exchanger 3 is lower than the lower limit of the working temperature of the coolant.

[0056] If it is in the reverse charging state, switch to the preheating bypass circulation mode; the judgment condition for the reverse charging state is: the outlet temperature of the indirect heat exchanger 3 is higher than the working fluid phase change temperature of the preheating accumulator 6, and the working fluid temperature of the preheating accumulator 6 is lower than its working fluid phase change temperature.

[0057] If it is in normal working condition, switch to air-cooled main circulation mode; the conditions for judging normal working condition are: the outlet temperature of the indirect heat exchanger 3 is not lower than the lower limit of the working temperature of the coolant, and not higher than the working fluid phase change temperature of the preheating accumulator 6.

[0058] If the temperature is too high, increase the power of the circulating pump 4 and the cooling fan 54. The condition for judging the temperature is: the outlet temperature of the partition heat exchanger 3 is higher than the upper limit of the coolant's operating temperature.

[0059] To cope with emergencies such as extreme low temperatures or incomplete charging of the preheating accumulator 6, the heat dissipation methods for the regenerative hydraulic system may also include:

[0060] Furthermore, the state of the hydraulic system also includes a preheating and charging state; further, the state of the hydraulic system also includes an insufficient preheating state; if it is in an insufficient preheating state, switch to the preheating bypass circulation mode and turn on the preheating heater.

[0061] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A heat dissipation device for a heat storage hydraulic system, characterized in that, include: The hydraulic oil storage tank (1) is equipped with an upper return port (11) and a lower outlet port (12); The coolant circulation pipeline (2) includes a hydraulic oil heat exchange section (21), an air-cooled heat dissipation section (22), a preheating section (23), a first three-way valve (24), and a second three-way valve (25); the upper ends of the hydraulic oil heat exchange section (21), the air-cooled heat dissipation section (22), and the preheating section (23) are respectively connected to the three ports of the first three-way valve (24); the lower ends of the hydraulic oil heat exchange section (21), the air-cooled heat dissipation section (22), and the preheating section (23) are respectively connected to the three ports of the second three-way valve (25). A partition wall heat exchanger (3) and a circulating pump (4) are connected in series on the hydraulic oil heat exchange pipe section (21). The partition wall heat exchanger (3) is arranged vertically inside the hydraulic oil storage tank (1). The coolant outlet of the partition wall heat exchanger (3) is at the top and the inlet is at the bottom. The circulating pump (4) is used to maintain the coolant in the partition wall heat exchanger (3) from bottom to top. An air-cooled radiator (5) is installed on the air-cooled heat dissipation pipe section (22). The air-cooled radiator (5) includes an upper manifold (51), a lower manifold (52), several parallel heat sinks (53), and a cooling fan (54). The heat sinks (53) are provided with vertically parallel coolant pipes (531). The upper ends of the coolant pipes (531) are all connected to the upper manifold (51), and the lower ends of the coolant pipes are all connected to the lower manifold (52). The surface of the heat sinks (53) is provided with an array of uniform temperature heat storage blocks (532). It contains a first phase change heat storage medium, the phase change temperature of which is the first phase change temperature, which is lower than the upper limit of the coolant's working temperature; the cooling fan (54) is installed directly above the heat sink (53), and an enclosed air duct is provided around the upper part of the cooling fan (54) and the heat sink (53), and a guide vane is provided around the lower part of the heat sink (53); the air outlet direction of the cooling fan (54) is vertically upward and parallel to the heat sink (53); A preheating accumulator (6) is installed on the preheating pipe section (23). The preheating accumulator (6) contains a second phase change heat storage medium, the phase change temperature of which is higher than the lower limit of the working temperature of the coolant. The phase change heat storage capacity of the preheating accumulator (6) is greater than the heat required for all hydraulic oils to rise from the local minimum temperature to the lower limit of the working temperature of the coolant. A preheating heater is also installed on the preheating pipe section (23). The intelligent monitoring component is preset with the working fluid phase change temperature, coolant working temperature lower limit and upper limit of the preheating accumulator (6), and is used to obtain the outlet temperature of the indirect heat exchanger (3) and the working fluid temperature of the preheating accumulator (6), and control the first three-way valve (24) and the second three-way valve (25) to make the coolant circulation pipeline (2) operate in a specific circulation mode; the specific circulation mode includes the air-cooled main circulation mode and the preheating bypass circulation mode; in the air-cooled main circulation mode, the hydraulic oil heat exchange pipe section (21) is connected to the air-cooled heat dissipation pipe section (22) and disconnected from the preheating pipe section (23); in the preheating bypass circulation mode, the hydraulic oil heat exchange pipe section (21) is connected to the preheating pipe section (23) and disconnected from the air-cooled heat dissipation pipe section (22); If the outlet temperature of the indirect heat exchanger (3) is lower than the lower limit of the working temperature of the coolant, adjust to the preheating bypass circulation mode; If the outlet temperature of the indirect heat exchanger (3) is not lower than the lower limit of the working temperature of the coolant and not higher than the phase change temperature of the working fluid in the preheating accumulator (6), adjust to the air-cooled main circulation mode. If the outlet temperature of the indirect heat exchanger (3) is higher than the working fluid phase change temperature of the preheating accumulator (6), and the working fluid temperature of the preheating accumulator (6) is lower than its working fluid phase change temperature, the preheating bypass circulation mode is switched. If the outlet temperature of the indirect heat exchanger (3) is higher than the working fluid phase change temperature of the preheating heat storage device (6), and the working fluid temperature of the preheating heat storage device (6) is not lower than its working fluid phase change temperature, the system is switched to the air-cooled main circulation mode. If the working fluid temperature of the preheating accumulator (6) is lower than the lower limit of the working temperature of the coolant, the intelligent monitoring component controls the preheating heater to turn on. The intelligent monitoring component is also used to control the power of the circulating pump (4) and the cooling fan (54); if the outlet temperature of the indirect heat exchanger (3) is higher than the upper limit of the working temperature of the coolant, the circulating pump (4) and the cooling fan (54) are controlled to increase their power.

2. The heat dissipation device for a regenerative hydraulic system according to claim 1, characterized in that, The preheating accumulator (6) includes several detachable heat storage components.

3. The heat dissipation device for a regenerative hydraulic system according to claim 2, characterized in that, The uniform temperature heat storage blocks (532) are arranged in a straight or staggered manner.

4. A heat dissipation method for a regenerative hydraulic system, used in the heat dissipation device for a regenerative hydraulic system as described in any one of claims 1 to 3, characterized in that, Includes the following steps: Obtain the working fluid phase change temperature, the lower limit and upper limit of the coolant working temperature of the preheating accumulator (6); Obtain the outlet temperature of the indirect heat exchanger (3) and the working fluid temperature of the preheating accumulator (6); Determine the state of the hydraulic system, which includes preheating state, reverse heating state, normal operation state, and over-temperature state; The circulation mode of the coolant circulation pipeline (2) and the power of the circulation pump (4) and the cooling fan (54) are controlled according to the state of the hydraulic system. If it is in the preheating state, adjust to the preheating bypass circulation mode; the judgment condition for the preheating state is: the outlet temperature of the indirect heat exchanger (3) is lower than the lower limit of the working temperature of the coolant; If it is in the reverse charging state, adjust to the preheating bypass circulation mode; the judgment condition of the reverse charging state is: the outlet temperature of the indirect heat exchanger (3) is higher than the working fluid phase change temperature of the preheating accumulator (6), and the working fluid temperature of the preheating accumulator (6) is lower than its working fluid phase change temperature. If it is in normal working condition, adjust to the air-cooled main circulation mode; the judgment condition for normal working condition is: the outlet temperature of the indirect heat exchanger (3) is not lower than the lower limit of the working temperature of the coolant, and not higher than the working fluid phase change temperature of the preheating accumulator (6); If the temperature is too high, increase the power of the circulating pump (4) and the cooling fan (54); the condition for judging the temperature is that the outlet temperature of the partition heat exchanger (3) is higher than the upper limit of the working temperature of the coolant.

5. The heat dissipation method for a regenerative hydraulic system according to claim 4, characterized in that, The hydraulic system can also be in a state of insufficient preheating. If it is in a state of insufficient preheating, it should be switched to the preheating bypass circulation mode and the preheating heater should be turned on.

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